Hobbing cutter type rock tunneling machine cutter head driving hydraulic system and tunneling equipment

Abstract

The utility model discloses a hob type rock tunneling machine cutterhead driving hydraulic system and tunneling equipment, and the system comprises a closed pump which is connected with a pressure oil source and provides power for the system, and the closed pump is provided with a variable cylinder; the hydraulic driving mechanism is connected with the closed pump, is used for being in driving connection with the cutterhead through the speed reducing mechanism and comprises a first driving element, a second driving element and a gear shifting element, and the gear shifting element is used for controlling an oil supply path of the first driving element to be connected or disconnected; preferably, the first driving element and the second driving element are hydraulic motors; in other embodiments, the first driving element and the second driving element can also be single-displacement motors; the reversing mechanism is used for controlling the variable cylinder to act so as to control the output flow and the output direction of the closed pump; and the variable control device is connected with the closed pump, the pressure oil source and the gear shifting element, and the variable control device is used for controlling the gear shifting element to act so as to control the oil supply way of the first driving element to be connected or disconnected.

Description

Technical Field

[0001] This utility model relates to the field of tunnel construction technology, and in particular, to a hydraulic system for driving the cutterhead of a rotary cutterhead rock tunneling machine. Furthermore, this utility model also relates to a tunneling device including the aforementioned hydraulic system for driving the cutterhead of a rotary cutterhead rock tunneling machine. Background Technology

[0002] The rotary cutterhead tunnel boring machine (TBM) is a specialized piece of equipment for tunneling hard rock. Its power head adopts the cutterhead structure of a tunnel boring machine (TBM), which is horizontally positioned for tunneling through hard rock geology, while also handling muck transport and bolt support operations. It is a continuous operation equipment integrating rock breaking, collection, material transport, and support. During construction, the cutterhead of the rotary cutterhead cuts through the hard rock, stripping away the muck and completing the tunnel excavation. With the development of tunnel construction technology, the functional requirements of construction equipment are to cope with diverse geological changes and the tunneling needs under different geological conditions, thereby meeting the requirements of equipment construction progress and efficiency. Therefore, the first domestic rotary cutterhead TBM was developed. The cutterhead system, as a key component of the rotary cutterhead TBM, is the most important part of this equipment, thus requiring extremely high standards for its drive control system.

[0003] Currently, there is relatively little information available on the technology of rotary cutter rock tunneling equipment. The cutterhead drive system, a key component of rotary cutter rock tunneling, evolved from shield tunneling or rock TBMs. Most shield tunneling or rock TBM cutterhead drive systems use direct drive from electric motors, while the use of hydraulic motors is relatively less common. The application of direct drive from electric motors in rotary cutter rock tunneling equipment has several drawbacks: low space utilization and a large proportion of the motors used. The large size of the electric motors increases the size of the cutterhead structure, affecting the overall machine layout; and a fixed, non-adjustable speed. The motor speed is fixed and cannot be infinitely adjusted, thus failing to meet the different needs of various working conditions. Under favorable working conditions, the motor output power is excessive, resulting in low energy utilization and high energy consumption. Utility Model Content

[0004] This utility model provides a hydraulic system for driving the cutterhead of a roller cutter rock tunneling machine and tunneling equipment to solve the technical problems of low space utilization, single speed without stepless adjustment, and poor adaptability to working conditions of existing roller cutter rock tunneling equipment.

[0005] According to one aspect of the present invention, a hydraulic system for driving the cutterhead of a rotary rock tunneling machine is provided, comprising:

[0006] A closed-loop pump, connected to a pressurized oil source, is used to provide power to the system; the closed-loop pump is equipped with a variable displacement cylinder.

[0007] A hydraulic drive mechanism, connected to a closed-loop pump and used for driving the cutter head via a reduction mechanism, includes a first drive element, a second drive element, and a gear shifting element, wherein the gear shifting element is used to control the connection or disconnection of the oil supply circuit of the first drive element.

[0008] A reversing mechanism is used to control the movement of the variable cylinder, thereby controlling the output flow and output direction of the closed pump;

[0009] A variable control device is connected to the closed pump, the pressure oil source, and the gear shifting element, respectively. The variable control device is used to control the operation of the gear shifting element and thereby control the connection or disconnection of the oil supply circuit of the first drive element.

[0010] As a further improvement to the above technical solution, the hydraulic system includes multiple hydraulic drive mechanisms and multiple closed-loop pumps; the hydraulic system also includes a multi-port block, which is connected to each of the closed-loop pumps and each of the hydraulic drive mechanisms respectively. The multi-port block is used to concentrate the pressure oil in the working oil circuit of the closed-loop pumps and distribute it to the input end of each of the hydraulic drive mechanisms, and is also used to concentrate the pressure oil in the return oil end of each of the hydraulic drive mechanisms and distribute it to the return oil end of each of the closed-loop pumps.

[0011] As a further improvement to the above technical solution, the gear switching element includes a first hydraulic directional valve, which is used to input the pressure oil of the closed pump to the first drive element and the second drive element under normal conditions, and is also used to switch the valve core position to disconnect the oil circuit between the closed pump and the first drive element under control oil input conditions.

[0012] As a further improvement to the above technical solution, the variable control device includes a first electromagnetic directional valve, which, when energized, allows the pressure oil to be output through the working oil circuit of the first electromagnetic directional valve to the control port of the first hydraulic directional valve; or, the variable control device includes a manual directional valve.

[0013] As a further improvement to the above technical solution, the variable control device also includes a pressure reducing valve for limiting the variables of the hydraulic drive mechanism and limiting the pressure of the reversing oil source of the closed pump to prevent overpressure.

[0014] As a further improvement to the above technical solution, the first electromagnetic directional valve is a two-position four-way electromagnetic directional valve or a two-position three-way electromagnetic directional valve.

[0015] As a further improvement to the above technical solution, the reversing mechanism includes a second electromagnetic reversing valve and a proportional hydraulic reversing valve disposed in the closed pump. The pressure oil source passes through the first working oil circuit of the second electromagnetic reversing valve to the first working oil circuit of the proportional hydraulic reversing valve and then to the rodless chamber of the variable cylinder. The pressure oil source passes through the second working oil circuit of the second electromagnetic reversing valve to the second working oil circuit of the proportional hydraulic reversing valve and then to the rod chamber of the variable cylinder.

[0016] As a further improvement to the above technical solution, the second electromagnetic directional valve is a three-position four-way electromagnetic directional valve.

[0017] As a further improvement to the above technical solution, the first driving element and the second driving element are hydraulic motors or single-displacement motors.

[0018] According to another aspect of the present invention, a tunneling device is also provided, which includes the above-described roller cutterhead drive hydraulic system for rock tunneling machines.

[0019] This utility model has the following beneficial effects:

[0020] The working principle of the hydraulic system driving the cutterhead of this rotary rock tunneling machine is as follows: Pressure oil is supplied from the variable displacement control device to the closed-loop pump, which outputs to the hydraulic drive mechanism, driving the first and second drive elements to rotate simultaneously. The pressure oil passing through the first and second drive elements circulates through the return oil circuit back to the closed-loop pump, maintaining the rotation of the first and second drive elements. This rotation, via the reduction mechanism, drives the cutterhead of the tunneling machine to rotate and perform work. In low-speed operation, the variable displacement control device drives the gear shifting element to low speed. The closed-loop pump outputs pressure oil to the first and second drive mechanisms and then circulates back, placing the hydraulic drive mechanism in a high-displacement, low-speed state. In high-speed operation, the variable displacement control device drives the hydraulic drive mechanism to rotate. When the gear shifting element is switched to high speed, the oil supply circuit of the first drive element is disconnected. The closed-loop pump outputs pressurized oil only to the second drive mechanism and then circulates back. The hydraulic drive mechanism is in a small displacement high-speed state. This system adopts a closed hydraulic system composed of a closed pump and a hydraulic drive mechanism. The space occupied by each component of the hydraulic drive mechanism is small, which can make the cutter head structure layout more compact and improve the applicability of working conditions. The hydraulic drive mechanism can realize two-level variable control, realize high and low speed switching, and switch according to different working conditions to improve energy utilization, energy saving effect and working efficiency. The reversing mechanism controls the action of the variable cylinder, thereby controlling the output flow and output direction of the closed-loop pump, realizing continuous speed adjustment of the cutter head within a wide range, making it more adaptable.

[0021] In addition to the objectives, features, and advantages described above, this utility model has other objectives, features, and advantages. The present utility model will now be described in further detail with reference to the figures. Attached Figure Description

[0022] The accompanying drawings, which form part of this application, are used to provide a further understanding of the present invention. The illustrative embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an undue limitation of the present invention. In the drawings:

[0023] Figure 1 This is a schematic diagram of the hydraulic system for driving the cutterhead of a rotary rock tunneling machine according to a preferred embodiment of this utility model.

[0024] Legend:

[0025] 1. Closed-loop pump; 101. Variable displacement cylinder; 102. Proportional hydraulic directional valve; 2. Reversing mechanism; 3. Variable displacement control device; 301. First solenoid directional valve; 302. Pressure reducing valve; 4. Hydraulic drive mechanism; 401. First hydraulic directional valve; 402. Second hydraulic directional valve; 403. First drive element; 404. Second drive element; 5. Multi-port block. Detailed Implementation

[0026] The embodiments of the present invention will be described in detail below with reference to the accompanying drawings. However, the present invention can be implemented in many different ways as defined and covered below.

[0027] Figure 1 This is a schematic diagram of the hydraulic system for driving the cutterhead of a rotary rock tunneling machine according to a preferred embodiment of this utility model.

[0028] like Figure 1 As shown, the hydraulic system for driving the cutterhead of the rotary rock tunneling machine in this embodiment includes:

[0029] Closed-loop pump 1 is connected to a pressure oil source to provide power to the system. Closed-loop pump 1 is equipped with a variable displacement cylinder 101.

[0030] The hydraulic drive mechanism 4 is connected to the closed pump 1 and is used to drive the cutter head via the reduction mechanism. It includes a first drive element 403, a second drive element 404, and a gear switching element. The gear switching element is used to control the connection or disconnection of the oil supply circuit of the first drive element 403.

[0031] The reversing mechanism 2 is used to control the action of the variable cylinder 101, thereby controlling the output flow and output direction of the closed pump 1.

[0032] The variable control device 3 is connected to the closed pump 1, the pressure oil source and the gear shifting element respectively. The variable control device 3 is used to control the action of the gear shifting element and thus control the oil supply circuit of the first drive element 403 to be connected or disconnected.

[0033] The cutterhead and reduction mechanism are implemented with reference to the existing tunneling machine structure, and will not be described in detail.

[0034] The working principle of the hydraulic system driving the cutterhead of this rotary cutterhead rock tunneling machine is as follows: Pressure oil from the source is output to the closed-loop pump 1 via the variable displacement control device 3, driving the first drive element 403 and the second drive element 404 to rotate simultaneously. The pressure oil passing through the first drive element 403 and the second drive element 404 circulates back to the closed-loop pump 1 via the return oil circuit, keeping the first drive element 403 and the second drive element 404 rotating. This rotation, via the reduction mechanism, drives the cutterhead of the tunneling machine to rotate and perform work. In low-speed mode, the variable displacement control device 3 drives the gear shifting element to low speed. The closed-loop pump 1 outputs pressure oil to the first and second drive mechanisms and then circulates back, keeping the hydraulic drive mechanism 4 in a high-displacement, low-speed state. In high-speed mode, the variable displacement control device... When the drive control gear switching element is set to high speed, the oil supply circuit of the first drive element 403 is disconnected. The closed pump 1 outputs pressurized oil only to the second drive mechanism and then returns the oil for circulation. The hydraulic drive mechanism 4 is in a small displacement high speed state. This system adopts a closed hydraulic system composed of closed pump 1 and hydraulic drive mechanism 4. The components of hydraulic drive mechanism 4 occupy little space, which can make the cutter head structure layout more compact and thus improve the applicability of working conditions. Hydraulic drive mechanism 4 can realize two-level variable control, realize high and low speed switching, and switch according to different working conditions to improve energy utilization, energy saving effect and working efficiency. The reversing mechanism 2 controls the action of variable cylinder 101, thereby controlling the output flow and output direction of closed pump 1, realizing continuous speed adjustment of cutter head within a wide range, and making it more adaptable.

[0035] Preferably, the first drive element 403 and the second drive element 404 are hydraulic motors.

[0036] In other embodiments, the first drive element 403 and the second drive element 404 may also be single-displacement motors;

[0037] In this embodiment, the hydraulic system includes multiple hydraulic drive mechanisms 4 and multiple closed-loop pumps 1; the hydraulic system also includes a multi-pass block 5, which connects each closed-loop pump 1 and each hydraulic drive mechanism 4 respectively. The multi-pass block 5 is used to concentrate and distribute the pressure oil from the working oil circuit of the closed-loop pump 1 to the input end of each hydraulic drive mechanism 4, and also to concentrate and distribute the pressure oil from the return end of each hydraulic drive mechanism 4 to the return end of each closed-loop pump 1.

[0038] In this embodiment, as Figure 1 As shown, the gear shifting element includes a first hydraulic directional valve 401, used to input pressure oil from the closed-loop pump 1 to the first drive element 403 and the second drive element 404 under normal conditions, and also used to switch the valve core position to disconnect the oil circuit between the closed-loop pump 1 and the first drive element 403 when control oil is input. For details, refer to... Figure 1The pressure oil at port A of the closed-loop pump 1 is output through the multi-port block 5 to the confluence of oil circuits R1 and R2. One path goes through the right position of the first hydraulic directional valve 401 to the upper chamber of the first drive element 403, and the other path is output to the upper chamber of the second drive element 404. The oil in the lower chambers of the first drive element 403 and the lower chambers of the second drive element 404 is led through the right position of the first hydraulic directional valve 401 to ports L1 and L2 respectively, reaching port B of the multi-port block 5 and then port B of the closed-loop pump 1, forming a closed loop. Preferably, the first hydraulic directional valve 401 is a two-position six-way hydraulic directional valve. (Reference) Figure 1 The hydraulic drive mechanism 4 also includes a second hydraulically controlled directional valve 402.

[0039] In this embodiment, as Figure 1 As shown, the variable control device 3 includes a first solenoid directional valve 301, which, when energized, outputs pressure oil through the working oil circuit of the first solenoid directional valve 301 to the control oil port of the first hydraulic directional valve 401. Specifically, when the first solenoid directional valve 301 is de-energized, its working oil circuit is in the right position under the action of spring force, and the control oil circuit acting on the first hydraulic directional valve 401 is in the open state. The pressure oil at the port of the closed pump 1A reaches the hydraulic motor R1 and R2 ports through the multi-port block 5 and then flows through the first hydraulic directional valve 401. After the directional valve 401 is in the right position, the oil reaches the upper chamber of the first drive element 403, while the other path goes directly to the upper chamber of the second drive element 404. The oil in the lower chamber of the first drive element 403 and the lower chamber of the second drive element 404 is led to ports L1 and L2 respectively through the right position of the first hydraulic directional valve 401, reaching port B of the multi-port block 5 and then port B of the closed pump 1. The hydraulic drive mechanism 4 is in a high-displacement, low-speed state. When the first electromagnetic directional valve 301 is energized, the electromagnetic force overcomes the spring force, causing the first electromagnetic directional valve 301 to operate in the left position. The pressurized oil source reaches the left position of the first solenoid directional valve 301, and then acts on the hydraulic control chamber of the first hydraulically controlled directional valve 401 in the hydraulic motor 4 through the Y port of the hydraulic drive mechanism 4. The hydraulic control force is greater than the spring force, causing the first hydraulically controlled directional valve 401 to work in the left position. The pressurized oil from the closed pump 1A port reaches the hydraulic motor R1 and R2 ports through the multi-port block 5, where they converge. One path is then cut off through the left position of the first hydraulically controlled directional valve 401, while the other path goes directly to the upper chamber of the second drive element 404. The oil in the lower chamber of the second drive element 404... The first hydraulic directional valve 401 leads to ports L1 and L2 respectively, reaching port B of the multi-port block 5 and then port B of the closed pump 1. The second drive element 404 rotates under the action of pressurized oil, while the first drive element 403 follows. The hydraulic drive mechanism 4 is in a low displacement high speed state. Preferably, the first solenoid directional valve 301 is a two-position four-way solenoid directional valve or a two-position three-way solenoid directional valve. In some embodiments, the first solenoid directional valve 301 can also be replaced with a manual directional valve, and the gear switching can be achieved by manual control.

[0040] In this embodiment, as Figure 1As shown, the variable control device 3 also includes a pressure reducing valve 302, which is used to limit the variable of the hydraulic drive mechanism 4 and limit the pressure of the switching oil source of the closed pump 1 to prevent overpressure and avoid damage to the hydraulic drive mechanism 4 and the closed pump 1.

[0041] In this embodiment, as Figure 1 As shown, the reversing mechanism 2 includes a second electromagnetic reversing valve and a proportional hydraulic reversing valve 102 disposed in the closed pump 1. The pressure oil source passes through the first working oil passage of the second electromagnetic reversing valve to the first working oil passage of the proportional hydraulic reversing valve 102 and then to the rodless chamber of the variable cylinder. The pressure oil source passes through the second working oil passage of the second electromagnetic reversing valve to the second working oil passage of the proportional hydraulic reversing valve 102 and then to the rod chamber of the variable cylinder. Preferably, the second electromagnetic reversing valve is a three-position four-way electromagnetic reversing valve. The proportional hydraulic directional valve 102 is a three-position, three-way proportional hydraulic directional valve 102. Specifically, when the left position of the three-position, four-way solenoid directional valve is energized, it operates in the left position. The pressure oil source passes through the pressure reducing valve 302 to the left position of the first solenoid directional valve 301, and then to the left chamber of the proportional hydraulic directional valve 102. The hydraulic control force in the left chamber is greater than the spring force in the right chamber, causing the proportional hydraulic directional valve 102 to operate in the left position. The internal oil circuit of the closed pump 1 reaches the variable oil level through the left position of the proportional hydraulic directional valve 102. The rodless chamber of the measuring cylinder 101 and the rod chamber oil flow through the left position of the proportional hydraulic control directional valve 102 to the rodless chamber of the variable cylinder 101, maintaining dynamic balance and causing the closed pump 1 to change direction, with high-pressure oil exiting from port A. When the right position of the three-position four-way solenoid directional valve is energized, it operates in the right position. The pressure oil source flows through the pressure reducing valve 302 to the right position of the first solenoid directional valve 301 and then to the right chamber of the proportional hydraulic control directional valve 102. The hydraulic control force in the right chamber is greater than the spring force in the left chamber, causing the proportional hydraulic control directional valve to... When 102 is in the right position, the internal oil circuit of the closed pump 1 directly reaches the rod chamber of the variable cylinder 101. The oil in the rodless chamber is drained after the proportional hydraulic control directional valve 102 is in the right position, causing the closed pump 1 to change variable, and high-pressure oil is discharged from port B. By controlling the displacement of the proportional pump group, the cutter head can be continuously adjusted in a wide range. By controlling the displacement of the two-point control type bidirectional variable motor, high and low speed switching can be achieved, resulting in high energy utilization, high working efficiency, and good system energy saving effect.

[0042] In the description of this utility model, it should be noted that the terms "upper", "lower", "front", "rear", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0043] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0044] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A hydraulic system for driving the cutterhead of a rotary cutter rock tunneling machine, characterized in that, include: A closed-loop pump (1) is connected to a pressure oil source to provide power to the system. The closed-loop pump (1) is equipped with a variable cylinder (101). The hydraulic drive mechanism (4) is connected to the closed pump (1) and is used to drive the cutter head via the reduction mechanism. It includes a first drive element (403), a second drive element (404), and a gear switching element. The gear switching element is used to control the connection or disconnection of the oil supply circuit of the first drive element (403). The reversing mechanism (2) is used to control the action of the variable cylinder (101) and thus control the output flow and output direction of the closed pump (1); The variable control device (3) is connected to the closed pump (1), the pressure oil source and the gear switching element respectively. The variable control device (3) is used to control the action of the gear switching element and thus control the oil supply circuit of the first drive element (403) to be connected or disconnected.

2. The hydraulic system for driving the cutterhead of a rotary rock tunnel boring machine according to claim 1, characterized in that, The hydraulic system includes multiple hydraulic drive mechanisms (4) and multiple closed pumps (1); the hydraulic system also includes a multi-pass block (5), which is connected to each of the closed pumps (1) and each of the hydraulic drive mechanisms (4). The multi-pass block (5) is used to concentrate the pressure oil in the working oil circuit of the closed pump (1) and distribute it to the input end of each of the hydraulic drive mechanisms (4), and is also used to concentrate the pressure oil in the return oil end of each of the hydraulic drive mechanisms (4) and distribute it to the return oil end of each of the closed pumps (1).

3. The hydraulic system for driving the cutterhead of a rotary rock tunnel boring machine according to claim 1, characterized in that, The gear shifting element includes a first hydraulic directional valve (401), which is used to input the pressure oil of the closed pump (1) to the first drive element (403) and the second drive element (404) under normal conditions, and is also used to switch the valve core position to disconnect the oil circuit between the closed pump (1) and the first drive element (403) under the control oil input state.

4. The hydraulic system for driving the cutterhead of a rotary rock tunnel boring machine according to claim 3, characterized in that, The variable control device (3) includes a first electromagnetic directional valve (301), which, when energized, outputs the pressure oil through the working oil circuit of the first electromagnetic directional valve (301) to the control port of the first hydraulic directional valve (401), or the variable control device (3) includes a manual directional valve.

5. The hydraulic system for driving the cutterhead of a rotary rock tunnel boring machine according to claim 4, characterized in that, The variable control device (3) also includes a pressure reducing valve (302) for limiting the variables of the hydraulic drive mechanism (4) and limiting the pressure of the switching oil source of the closed pump (1) to prevent overpressure.

6. The hydraulic system for driving the cutterhead of a rotary rock tunnel boring machine according to claim 4, characterized in that, The first solenoid directional valve (301) is a two-position four-way solenoid directional valve or a two-position three-way solenoid directional valve.

7. The hydraulic system for driving the cutterhead of a rotary rock tunnel boring machine according to claim 1, characterized in that, The reversing mechanism (2) includes a second electromagnetic reversing valve and a proportional hydraulic reversing valve (102) disposed in the closed pump (1). The pressure oil source passes through the first working oil passage of the second electromagnetic reversing valve to the first working oil passage of the proportional hydraulic reversing valve (102) to the rodless chamber of the variable cylinder. The pressure oil source passes through the second working oil passage of the second electromagnetic reversing valve to the second working oil passage of the proportional hydraulic reversing valve (102) to the rod chamber of the variable cylinder.

8. The hydraulic system for driving the cutterhead of a rotary rock tunnel boring machine according to claim 7, characterized in that, The second solenoid directional valve is a three-position four-way solenoid directional valve.

9. The hydraulic system for driving the cutterhead of a rotary cutterhead rock tunneling machine according to any one of claims 1-8, characterized in that, The first drive element (403) and the second drive element (404) are hydraulic motors or single-displacement motors.

10. A tunneling device, characterized in that, The application has the cutterhead drive hydraulic system of the rotary rock tunneling machine according to any one of claims 1-9.

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