Combined propelling hydraulic system for chambering type vertical shaft heading machine

Abstract

The utility model provides a combined propelling hydraulic system for a chambering type vertical shaft heading machine. The combined propelling hydraulic system comprises a motor, a propelling pump, a control oil pump, a hydraulic oil tank, a propelling control valve group, an oil cylinder pressure maintaining valve group and a propelling oil cylinder, one end of the thrust cylinder is connected with the vertical shaft heading machine tight supporting platform, and the other end is connected with the main driver and the cutterhead; the oil cylinder pressure maintaining valve group is integrated on the propulsion oil cylinder and is connected with the propulsion control valve group through a steel pipe; the propulsion control valve group comprises a proportional speed regulating valve and a proportional overflow valve and is used for realizing a speed control mode and a pressure control mode of the propulsion oil cylinder; the oil cylinder pressure maintaining valve set comprises an external control one-way valve and a pilot-operated type overflow valve and is used for maintaining the pressure maintaining state of an oil cylinder during step changing, cutter head retreating and pipeline accidental damage. A rod cavity of the thrust cylinder is provided with a back pressure system, and back pressure is adjusted through an overflow valve to reduce vibration impact of equipment. The utility model can effectively improve the unfavorable geology handling capacity of equipment, reduce high-pressure impact, and enhance the safety and stability of the equipment.

Description

Technical Field

[0001] This utility model relates to the field of construction equipment for reaming shaft tunneling machines, specifically a combined propulsion hydraulic system for reaming shaft tunneling machines. Background Technology

[0002] With the continuous development of water conservancy and tunnel projects in my country, the requirements for construction equipment are constantly increasing, and the construction equipment and technology related to tunnel excavation have been greatly developed. Among them, shaft boring machines, as a new type of tunnel construction equipment, are attracting more and more attention due to their characteristics of speed, efficiency, safety, and high level of informatization and automation, and their application scope has been gradually expanding in recent years. Expanding shaft boring machines, in conjunction with already constructed pilot shafts, are generally used in strata with relatively intact rock formations. With appropriate support and auxiliary methods, they can also be used in some soft rock strata. The main working mechanism is to use the support shoes on both sides of the equipment to tighten the tunnel wall and provide fulcrum, and then propel the machine forward through reaction force and gravity.

[0003] Prior art document CN114810703A discloses a hydraulic system for step-changing control of a vertical shaft tunneling machine. The protected scope of this type of tunneling machine propulsion system includes: a first oil pump, a first directional valve, a hydraulically controlled check valve, and a propulsion cylinder. The first oil pump is connected to the first directional valve, the first directional valve is connected to the hydraulically controlled check valve, the hydraulically controlled check valve is connected to the rod-side and rodless-side chambers of the propulsion cylinder, and an electromagnetic ball valve and a first proportional relief valve are connected in the oil line connecting the hydraulically controlled check valve to the rodless-side chamber of the propulsion cylinder. It also includes a second oil pump and a second directional valve. The lifting cylinder is equipped with a second oil pump powered by a variable frequency motor. The second oil pump is connected to a second directional valve, which in turn connects to the rod-side and rodless-side chambers of the lifting cylinder. A hydraulically controlled check valve maintains the thrust force, preventing sudden pressure release from the thrust cylinder during step-changing. Furthermore, an electromagnetic ball valve and a first proportional relief valve facilitate overflow and unloading, ensuring smooth step-changing operations and improving the stability and safety of the hydraulic system. However, the system suffers from drawbacks, including susceptibility to pressure loss in case of pipe rupture and a lack of multi-mode propulsion functionality.

[0004] Therefore, based on the actual working conditions on site, a combined propulsion hydraulic system for reaming shaft tunneling machines is proposed to solve the above problems. Summary of the Invention

[0005] The purpose of this invention is to provide a combined propulsion hydraulic system for a borehole-expanding vertical shaft tunneling machine, which solves problems such as attitude stability, multi-mode propulsion, and vibration control when pipelines burst.

[0006] To solve the aforementioned technical problems, the present invention adopts the following technical solution: a combined propulsion hydraulic system for a borehole-expanding vertical shaft tunneling machine, comprising: a motor, a propulsion pump, a control oil pump, a hydraulic oil tank, a propulsion control valve group, a cylinder pressure maintaining valve group, and a propulsion cylinder; one end of the propulsion cylinder is connected to the shaft tunneling machine's support platform, and the other end is connected to the main drive and cutterhead; the cylinder pressure maintaining valve group is integrated on the propulsion cylinder and connected to the propulsion control valve group via a steel pipe; the propulsion control valve group includes a proportional speed regulating valve and a proportional relief valve, used to realize the speed control mode and pressure control mode of the propulsion cylinder; the cylinder pressure maintaining valve group includes an externally controlled check valve and a pilot-operated relief valve, used to maintain the cylinder pressure during step changes, cutterhead retraction, and accidental pipeline damage; the rod chamber of the propulsion cylinder is equipped with a back pressure system, which adjusts the back pressure through the relief valve to reduce equipment vibration and impact.

[0007] Preferably, the propulsion control valve group also includes a check valve, a pressure reducing valve, a throttle valve, a three-way solenoid ball valve, a solenoid directional valve, and an electro-hydraulic directional valve, for realizing independent control of the cylinder action and multi-channel oil supply.

[0008] Preferably, port P6-1 of the propulsion control valve group is connected to the propulsion pump, port P6-2 is connected to the control oil pump, ports T6 and D6-1 are connected to the hydraulic oil tank, and ports P6-5 to P6-16 are connected to the rod-side and rodless-side chambers of each propulsion cylinder, respectively.

[0009] Preferably, the oil ports P15-1 and P15-2 of the cylinder pressure holding valve assembly are connected to the rodless chamber and rod chamber of the propulsion cylinder, respectively, and the oil ports P15-3 and P15-4 are connected to the pressure holding control oil circuit of the propulsion control valve assembly, respectively.

[0010] Preferably, the back pressure system includes an overflow valve disposed in the rod chamber of the propulsion cylinder, the set pressure of which is adjustable to balance the weight of the equipment and reduce impact.

[0011] Preferably, the propulsion cylinders are grouped together, and the pressure holding valve group of each group of cylinders is independently controlled, and the propulsion pressure and speed can be set separately.

[0012] Preferably, the hydraulic cylinder pressure holding valve assembly can maintain the pressure holding state through the pilot-operated relief valve when the equipment is powered off, preventing the equipment from losing pressure and falling.

[0013] Preferably, the propulsion control valve group adopts a modular multi-way valve design, in which any one link can be disassembled and replaced individually.

[0014] Preferably, the set pressure of the proportional relief valve and the flow rate of the proportional speed control valve are adjusted in coordination to achieve propulsion mode switching and ultimate thrust control.

[0015] Preferably, the leakage port D15-1 of the cylinder pressure holding valve assembly is connected to the hydraulic oil tank through an independent pipeline to prevent leakage oil from contaminating the main circuit.

[0016] The present invention has the following beneficial effects:

[0017] 1. This utility model integrates a hydraulic cylinder pressure maintaining valve assembly onto the propulsion cylinder, with a steel pipe connecting the middle pipe, eliminating the possibility of accidental pipe damage or bursting; the pressure maintaining design of the valve assembly ensures that the entire propulsion system can maintain a pressure-holding state, ensuring that the system will not experience pressure loss and fall, greatly improving the safety of the equipment.

[0018] 2. In this utility model, the speed and pressure of a single propulsion cylinder can be controlled independently, improving the operational flexibility of the equipment;

[0019] 3. This invention allows for proportional adjustment of the descent speed during the step-change descent process, reducing impact;

[0020] 4. This utility model can provide two propulsion modes for the propulsion system: pressure and speed. Different propulsion modes can be selected and adjusted flexibly according to the geological conditions on site.

[0021] 5. The propulsion valve assembly of this utility model adopts a multi-way valve design, which allows for the individual disassembly of any one section, facilitating replacement and maintenance; it also provides a convenient way for future modifications such as adding or removing propulsion cylinders.

[0022] 6. During high-risk actions such as propulsion, step change, and cutter head retraction, the pressure holding system of this utility model is in working condition throughout the entire process. The set pressure of the pressure holding valve is sufficient to support the weight of the equipment, ensuring that the equipment will not lose control due to its own weight, and that the operation is stable and the speed is linearly controllable. Furthermore, it can maintain the current state for a long time in the event of an unexpected power outage. Attached Figure Description

[0023] Figure 1 This is a schematic diagram of the hydraulic system of this utility model;

[0024] Figure 2 This is a schematic diagram of the oil inlet connection principle of the propulsion control valve group in this utility model;

[0025] Figure 3 This is a schematic diagram of the working principle of the propulsion control valve group in this utility model;

[0026] Figure 4 This is a schematic diagram of the hydraulic cylinder pressure maintaining valve assembly in this utility model. Detailed Implementation

[0027] The present invention will be further described below with reference to the accompanying drawings and embodiments:

[0028] Please see the appendix Figures 1 to 4This utility model provides a combined propulsion hydraulic system for a borehole-expanding vertical shaft tunneling machine, including: a motor 1, a propulsion pump 2, a control oil pump 3, a hydraulic oil tank 4, a propulsion control valve group 6, a cylinder pressure maintaining valve group 15, and a propulsion cylinder 22; one end of the propulsion cylinder 22 is connected to the shaft tunneling machine's support platform, and the other end is connected to the main drive and cutterhead; the cylinder pressure maintaining valve group 15 is integrated on the propulsion cylinder 22 and connected to the propulsion control valve group 6 through a steel pipe; the propulsion control valve group 6 includes a proportional speed regulating valve 12 and a proportional relief valve 13, used to realize the speed control mode and pressure control mode of the propulsion cylinder 22; the cylinder pressure maintaining valve group 15 includes an externally controlled one-way valve 18 and a pilot-operated relief valve 19, used to maintain the cylinder pressure in the event of step change, cutterhead retraction, or accidental pipeline damage; the rod chamber of the propulsion cylinder 22 is equipped with a back pressure system, and the back pressure is adjusted by the relief valve 20 to reduce equipment vibration and impact.

[0029] Preferably, the propulsion control valve group 6 further includes a one-way valve 7, a pressure reducing valve 8, a throttle valve 9, a three-way solenoid ball valve 10, a solenoid directional valve 11, and an electro-hydraulic directional valve 14, for realizing independent control of the cylinder action and multi-way oil supply.

[0030] Preferably, port P6-1 of the propulsion control valve group 6 is connected to the propulsion pump 2, port P6-2 is connected to the control oil pump 3, ports T6 and D6-1 are connected to the hydraulic oil tank 4, and ports P6-5 to P6-16 are respectively connected to the rod chamber and rodless chamber of each propulsion cylinder 22.

[0031] Preferably, the oil ports P15-1 and P15-2 of the cylinder pressure holding valve group 15 are connected to the rodless chamber and rod chamber of the propulsion cylinder 22, respectively, and the oil ports P15-3 and P15-4 are connected to the pressure holding control oil circuit of the propulsion control valve group 6, respectively.

[0032] Preferably, the back pressure system includes an overflow valve 20 disposed in the rod chamber of the propulsion cylinder 22. The set pressure of the overflow valve 20 is adjustable to balance the weight of the equipment and reduce impact.

[0033] Preferably, there are 6 sets of propulsion cylinders 22, and the pressure holding valve group 15 of each set of cylinders is independently controlled, and the propulsion pressure and speed can be set separately.

[0034] Preferably, the hydraulic cylinder pressure holding valve assembly 15 can still maintain the pressure holding state through the pilot-operated relief valve 19 when the equipment is powered off, so as to prevent the equipment from losing pressure and falling.

[0035] Preferably, the propulsion control valve group 6 adopts a modular multi-way valve design, in which any one link can be disassembled and replaced individually.

[0036] Preferably, the set pressure of the proportional relief valve 13 is coordinated with the flow rate of the proportional speed control valve 12 to achieve propulsion mode switching and ultimate thrust control.

[0037] Preferably, the leakage port D15-1 of the cylinder pressure holding valve assembly 15 is connected to the hydraulic oil tank 4 through an independent pipeline to avoid leakage oil contaminating the main circuit.

[0038] The system working modes of this utility model are divided into speed control mode propulsion, pressure control mode propulsion, step change, platform lowering, and cutter head retraction. Specific embodiments are as follows:

[0039] Example 1 describes the propulsion mode and the ultimate thrust mode: Propulsion pump 2 supplies oil to port P6-1 of propulsion control valve group 6 via safety valve 5-1 to provide the power source for the propulsion cylinder's operation; control oil pump 3 supplies constant pressure oil to port P6-2 of propulsion control valve group 6 via safety valve 5-2 to provide the power source for the hydraulic control valve; high-pressure oil from propulsion pump 2 enters the working link of propulsion control valve group 6 through check valve 7-1, and according to the description of cylinder group 1's operation, cylinder groups 2-6... The cylinder operates in the same way, through the proportional speed control valve 12-1, check valve 7-2, and hydraulic directional valve 14-1; the oil source of the control oil pump 3 passes through the pressure reducing valve 8 and throttle valve 9 to the solenoid directional valve 11; when the solenoid directional valve 11 is de-energized, the control oil source enters the working link of the propulsion control valve group 6 through the solenoid directional valve 11, and controls the electro-hydraulic directional valve 14-1 to move to the left position. The high-pressure oil source of the proportional speed control valve 12-1 flows to the oil port P6-5 through the hydraulic directional valve 14-1. The oil enters the cylinder pressure holding valve group 15 through a high-pressure oil pipe at port P15-1, then passes through the external control check valve 18-1 into the rodless chamber of the propulsion cylinder 22-1, completing the propulsion action. The oil in the rod chamber of the propulsion cylinder 22 returns by overcoming the set pressure of the relief valve 20-1. After passing through the relief valve 20-1, it enters the high-pressure oil pipe through port P15-2, flows through port P6-6 back to the propulsion control valve group 6, passes through the electro-hydraulic directional valve 14 into the return oil circuit, and returns to the oil tank through port T6. The proportional speed control valve 12-1 and the proportional relief valve 13-1 can be used to control the speed and inlet pressure of the propulsion cylinder. When the equipment is in pressure propulsion mode, the proportional speed control valve 12-1 is set to the maximum propulsion speed, and the proportional relief valve 13-1 adjusts the propulsion pressure of the hydraulic cylinder according to the signal. When the equipment is in speed propulsion mode, the proportional relief valve 13-1 is set to the maximum propulsion pressure. Different speeds are set through the proportional speed control valve 12-1 to adjust the movement of the propulsion cylinder and complete the tunneling. Propulsion cylinders 22-1 to 22-6 can be individually set with different propulsion pressures and speeds. If the ultimate thrust mode is required, the three-way solenoid ball valve 10-1 can be energized, and control oil enters the P15-3 port of the cylinder pressure holding valve group 15 through port P6-3, opening the external control check valve 18-2 and closing the rod chamber pressure holding of the propulsion cylinder. At this time, the propulsion cylinder is in a no-back-pressure mode, and all the pressure in the rodless chamber is converted into the thrust of the propulsion cylinder. The effective thrust of the equipment is calculated based on the pressure value fed back by the pressure sensor 21-1.

[0040] Example 2 describes the step-changing mode: after the shaft boring machine's tensioning cylinder is relaxed, the propulsion cylinder is retracted, and the tensioning platform descends. At this time, propulsion pump 2 supplies oil to port P6-1 of propulsion control valve group 6 through safety valve 5-1 to provide the power source for propulsion cylinder operation; control oil pump 3 supplies constant pressure oil to port P6-2 of propulsion control valve group 6 through safety valve 5-2 to provide the power source for hydraulic control valve; high pressure oil from propulsion pump 2 enters the working link of propulsion control valve group 6 through check valve 7-1. According to the operation instructions of cylinder group 1, cylinders 2-6 operate in the same way, passing through proportional speed control valve 12-1, check valve 7-2, and hydraulic control directional valve 14-1; oil from control oil pump 3 passes through pressure reducing valve 8 and throttle valve 9 to solenoid directional valve 11; solenoid directional valve 11 is energized, and control oil enters the working link of propulsion control valve group 6 through solenoid directional valve 11, controlling electro-hydraulic directional valve 14-1 to move to the right position, and high pressure oil from proportional speed control valve 12-1 flows through solenoid directional valve 14-1 to Oil port P6-6 enters the P15-2 oil port of cylinder pressure holding valve group 15 through high-pressure oil pipe, and enters the rod chamber of propulsion cylinder 22-1 through external control check valve 18-2. The propulsion cylinder retracts, supports the platform and falls, completing the step change action. The pressure oil in the rodless chamber of the propulsion cylinder returns through the pilot-operated relief valve 19. When the solenoid ball valve 16-1 is de-energized, the pilot circuit of the pilot-operated relief valve 19 is closed. At this time, the opening pressure of the pilot-operated relief valve 19 is the maximum propulsion pressure of the equipment, maintaining the posture of the equipment after propulsion. During the step change, the solenoid ball valve 16-1 is energized, and the pilot pressure of the pilot-operated relief valve 19 is determined by the relief valve 17-1. At this time, the set pressure of the rodless chamber only maintains the self-weight of the equipment. The high-pressure oil in the rodless chamber overcomes the set pressure of the pilot-operated relief valve 19 to complete the step change operation, ensuring that the rodless chamber side has sufficient capacity to maintain the self-weight of the equipment when the action stops at any time during the step change process.

[0041] Example 3 describes the cutterhead retraction mode: After the shaft boring machine's support cylinder is tightened, the propulsion cylinder retracts, and the cutterhead retracts. At this time, propulsion pump 2 supplies oil to port P6-1 of propulsion control valve group 6 through safety valve 5-1 to provide the power source for the propulsion cylinder's movement; control oil pump 3 supplies constant pressure oil to port P6-2 of propulsion control valve group 6 through safety valve 5-2 to provide the power source for the hydraulic control valve; high-pressure oil from propulsion pump 2 enters the working link of propulsion control valve group 6 through check valve 7-1. According to the description of cylinder group 1's movement, cylinders 2-6 have the same movement method, passing through proportional speed control valve 12-1, check valve 7-2, and hydraulic control directional valve 14-1; the oil source from control oil pump 3 passes through pressure reducing valve 8 and throttle valve 9 to solenoid directional valve 11; solenoid directional valve 11 is energized, and the control oil source... The oil enters the working link of the propulsion control valve group 6 through the solenoid directional valve 11, controlling the electro-hydraulic directional valve 14-1 to move to the right position. The high-pressure oil source, after passing through the proportional speed control valve 12-1, flows through the directional valve 14-1 to the oil port P6-6, enters the oil port P15-2 of the cylinder pressure maintaining valve group 15 through the high-pressure oil pipe, and enters the rod chamber of the propulsion cylinder 22-1 through the external control check valve 18-2. The propulsion cylinder retracts, the solenoid ball valve 16-1 is energized, and the pilot pressure of the pilot-operated relief valve 19 is determined by the relief valve 17-1. At this time, the set pressure of the rodless chamber only maintains the weight of the equipment. The high-pressure oil in the rodless chamber overcomes the set pressure of the pilot-operated relief valve 19 to complete the cutter head retraction operation. At this time, the cutter head is in a suspended state. Through the pressure holding circuit composed of the external control check valve 18-2 and the relief valve 20-2, the cylinder is kept from falling. The set pressure of the relief valve 20-1 only maintains the weight of the cutter head + the main drive.

[0042] The above embodiments are merely preferred technical solutions of this utility model and should not be considered as limitations on this utility model. The protection scope of this utility model should be the technical solution described in the claims, including equivalent substitutions of the technical features described in the claims. That is, equivalent substitutions and improvements within this scope are also within the protection scope of this utility model.

Claims

1. A combined propulsion hydraulic system for a raise boring machine, characterized in that, It comprises: The motor, the propelling pump, the control oil pump, the hydraulic oil tank, the propelling control valve group, the oil cylinder pressure maintaining valve group, the propelling oil cylinder; one end of the propelling oil cylinder is connected with the shaft sinking machine supporting platform, and the other end is connected with the main drive and the cutter head; the oil cylinder pressure maintaining valve group is integrated on the propelling oil cylinder and is connected with the propelling control valve group through a steel pipe; the propelling control valve group comprises a proportional speed regulating valve and a proportional overflow valve, which are used for realizing the speed control mode and the pressure control mode of the propelling oil cylinder; the oil cylinder pressure maintaining valve group comprises an external control check valve and a pilot overflow valve, which are used for maintaining the pressure maintaining state of the oil cylinder when the step is changed, the cutter head is retreated and the pipeline is accidentally damaged; the rod cavity of the propelling oil cylinder is provided with a back pressure system, and the back pressure is adjusted through the overflow valve to reduce the vibration impact of the equipment.

2. A combined propulsion hydraulic system for a raise boring machine according to claim 1, characterized in that, The propelling control valve group further comprises a check valve, a pressure reducing valve, a throttle valve, a three-way electromagnetic ball valve, an electromagnetic reversing valve and an electro-hydraulic reversing valve, which are used for realizing the independent control and multi-way oil supply of the oil cylinder action.

3. A combined propulsion hydraulic system for a raise boring machine according to claim 2, characterized in that, The oil port P6-1 of the propelling control valve group is connected with the propelling pump, the oil port P6-2 is connected with the control oil pump, the oil ports T6 and D6-1 are connected with the hydraulic oil tank, and the oil ports P6-5 to P6-16 are respectively connected with the rod cavity and the rodless cavity of each propelling oil cylinder.

4. A combined propulsion hydraulic system for a raise boring machine as defined in claim 1, characterized in that, The oil ports P15-1 and P15-2 of the oil cylinder pressure maintaining valve group are respectively connected with the rodless cavity and the rod cavity of the propelling oil cylinder, and the oil ports P15-3 and P15-4 are respectively connected with the pressure maintaining control oil circuit of the propelling control valve group.

5. A combined propulsion hydraulic system for a raise boring machine as defined in claim 1, characterized in that, The back pressure system comprises an overflow valve arranged in the rod cavity of the propelling oil cylinder, and the set pressure of the overflow valve is adjustable to balance the dead weight of the equipment and reduce the impact.

6. A combined propulsion hydraulic system for a raise boring machine as defined in claim 1, characterized in that, The propelling oil cylinder is 6 groups, the pressure maintaining valve group of each group of oil cylinder is independently controlled, and the propelling pressure and speed can be individually set.

7. A combined propulsion hydraulic system for a raise boring machine as defined in claim 1, characterized in that, The oil cylinder pressure maintaining valve group can still maintain the pressure maintaining state through the pilot overflow valve when the equipment is powered off, so as to prevent the equipment from falling down due to pressure loss.

8. A combined propulsion hydraulic system for a raise boring machine as defined in claim 1, characterized in that, The propelling control valve group adopts a modular multi-way valve design, and any connection can be individually detached and replaced.

9. A combined propulsion hydraulic system for a raise boring machine as defined in claim 1, wherein, The set pressure of the proportional overflow valve is cooperatively adjusted with the flow of the proportional speed regulating valve to realize the propelling mode switching and the limit thrust control.

10. A combined propulsion hydraulic system for a raise boring machine as defined in claim 1, characterized in that, The leakage oil port D15-1 of the oil cylinder pressure maintaining valve group is connected to the hydraulic oil tank through an independent pipeline, so as to avoid the pollution of the main circuit by the leakage oil.

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