Hydraulic propulsion system of shield tunneling machine and shield tunneling machine

Abstract

The utility model discloses a kind of shield machine hydraulic propulsion system and shield machine, wherein, the shield machine hydraulic propulsion system includes for being connected with the initiative control oil circuit of first oil cylinder and for being connected with the following control oil circuit of second oil cylinder;Initiative control oil circuit includes for being set between the first propulsion oil circuit of hydraulic pump and the rodless chamber of first oil cylinder, first propulsion oil circuit includes proportioning speed regulating valve, proportioning pressure reducing valve and first ball valve arranged in sequence;Following control oil circuit includes for being set between the second propulsion oil circuit of hydraulic pump and the rodless chamber of second oil cylinder, second propulsion oil circuit includes second ball valve and pilot pressure reducing valve arranged in sequence, the control end of pilot pressure reducing valve is connected with the output end of proportioning pressure reducing valve, to make the propulsion pressure and propulsion speed of second propulsion oil circuit all keep consistent relative to first propulsion oil route.The shield machine hydraulic propulsion system provided by the utility model can reduce the use quantity of proportioning speed regulating valve and proportioning pressure reducing valve, simple structure and low in cost.

Description

Technical Field

[0001] This utility model relates to the field of tunnel boring machine technology, and in particular, to a hydraulic propulsion system for a tunnel boring machine, and a tunnel boring machine using the said hydraulic propulsion system. Background Technology

[0002] Currently, when basic engineering projects such as subways, highways, railways, and water diversion projects need to cross large rivers, slurry balance shield tunneling machines are generally used to construct tunnels. Due to the large number and size of the propulsion cylinders in large-diameter slurry balance shield tunnels, in order to ensure that the shield machine has a certain propulsion speed, traditional hydraulic propulsion systems usually use multiple proportional speed control valves in parallel for speed control and parallel proportional pressure reducing valves or proportional relief valves for pressure control. Each propulsion cylinder needs to be equipped with a proportional speed control valve, proportional pressure reducing valve, or proportional relief valve. For example, Chinese invention patent CN114857491A provides a tunneling machine propulsion control system and tunneling machine. Its tunneling machine propulsion control system includes multiple cylinder control valve groups. Each cylinder control valve group has a propulsion oil circuit between it and the corresponding cylinder. The oil inlet and return of each cylinder are distributed and controlled by multiple cylinder control valve groups. This design method is not only costly, has a high failure rate, and is difficult to maintain, but also has a large control valve block, which is inconvenient to install and reduces the aesthetic coordination of the whole machine.

[0003] In addition, there is another type of shield machine hydraulic control system that adopts a single-zone single-pump form. Each group of propulsion cylinders is equipped with a set of hydraulic pumps. The propulsion speed and propulsion pressure of the hydraulic cylinders are controlled by pump control. Compared with the traditional control method, although this control method has improved control accuracy, the design cost and failure rate will also be greatly increased. The number of hydraulic pump sets required will increase many times over, which greatly increases the design difficulty of the hydraulic pump station. Utility Model Content

[0004] The present invention primarily provides a hydraulic propulsion system for tunnel boring machines (TBMs) to solve the technical problems of complex structure, high cost, and high failure rate of existing hydraulic control systems for multiple propulsion cylinders in TBMs.

[0005] This utility model also provides a tunnel boring machine that uses the above-mentioned tunnel boring machine hydraulic propulsion system.

[0006] According to one aspect of the present invention, a shield machine hydraulic propulsion system is provided for controlling multiple propulsion cylinders, wherein the multiple propulsion cylinders are respectively designated as a first cylinder and a second cylinder, and the shield machine hydraulic propulsion system includes an active control oil circuit for connecting to the first cylinder and a follower control oil circuit for connecting to the second cylinder.

[0007] The active control oil circuit includes a first propulsion oil circuit disposed between the hydraulic pump and the rodless chamber of the first cylinder. The first propulsion oil circuit includes a proportional speed control valve, a proportional pressure reducing valve and a first ball valve disposed in sequence. The proportional speed control valve is used to control the propulsion speed of the first cylinder and the proportional pressure reducing valve is used to control the propulsion pressure of the first cylinder.

[0008] The following control oil circuit includes a second propulsion oil circuit disposed between the hydraulic pump and the rodless chamber of the second cylinder. The second propulsion oil circuit includes a second ball valve and a pilot pressure reducing valve disposed in sequence. The control end of the pilot pressure reducing valve is connected to the output end of the proportional pressure reducing valve so that the propulsion pressure and propulsion speed of the second propulsion oil circuit are consistent with those of the first propulsion oil circuit.

[0009] Preferably, both the active control oil circuit and the follow control oil circuit include a first two-way cartridge valve and a first solenoid directional valve. The first solenoid directional valve is connected to the control terminal of the first two-way cartridge valve and is used to control the on / off state of the first two-way cartridge valve.

[0010] The first two-way cartridge valve in the active control oil circuit is used to connect the hydraulic pump and the rodless chamber of the first cylinder to control the oil intake of the rodless chamber of the first cylinder. The first two-way cartridge valve in the follow control oil circuit is used to connect the hydraulic pump and the rodless chamber of the second cylinder to control the oil intake of the rodless chamber of the second cylinder.

[0011] Preferably, both the active control oil circuit and the follow control oil circuit include a second two-way cartridge valve and a second solenoid directional valve. The second solenoid directional valve is connected to the control terminal of the second two-way cartridge valve and is used to control the on / off state of the second two-way cartridge valve.

[0012] The second two-way cartridge valve in the active control oil circuit is used to connect the oil tank and the rodless chamber of the first oil cylinder to control the return oil from the rodless chamber of the first oil cylinder. The second two-way cartridge valve in the follow control oil circuit is used to connect the oil tank and the rodless chamber of the second oil cylinder to control the return oil from the rodless chamber of the second oil cylinder.

[0013] Preferably, both the active control oil circuit and the follower control oil circuit include control branches. The first end of the control branch is provided with a first check valve for connection to a hydraulic pump, and the second end of the control branch is provided with a second check valve for connection to the rodless chamber of the corresponding propulsion cylinder. The control ends of the first solenoid directional valve and the second solenoid directional valve located in the same control oil circuit are arranged in parallel and are both connected to the third end of the control branch. The hydraulic direction of the first check valve and the second check valve is both oriented towards the third end of the control branch.

[0014] Preferably, both the active control oil circuit and the follow control oil circuit include a third solenoid directional valve, and a third two-way cartridge valve and a fourth two-way cartridge valve respectively connected to the third solenoid directional valve. The third solenoid directional valve is used to switchably control one of the third two-way cartridge valve and the fourth two-way cartridge valve to be open and the other to be closed.

[0015] The third two-way cartridge valve of the active control oil circuit is used to be installed between the hydraulic pump and the rod chamber of the first cylinder; the fourth two-way cartridge valve of the active control oil circuit is used to be installed between the oil tank and the rod chamber of the first cylinder; the third two-way cartridge valve of the follow control oil circuit is used to be installed between the hydraulic pump and the rod chamber of the second cylinder; and the fourth two-way cartridge valve of the follow control oil circuit is used to be installed between the oil tank and the rod chamber of the second cylinder.

[0016] Preferably, both the active control oil circuit and the follow control oil circuit include a safety valve, which is installed between the rod chamber of the corresponding propulsion cylinder and the oil tank.

[0017] Preferably, the active control circuit further includes a pressure sensor for connection to the rodless chamber of the first cylinder.

[0018] Preferably, the active control circuit further includes a third check valve disposed between the first ball valve and the rodless chamber of the first cylinder, and the follow control circuit further includes a fourth check valve disposed between the pilot pressure reducing valve and the rodless chamber of the second cylinder.

[0019] Preferably, the active control oil circuit further includes a third ball valve disposed between the hydraulic pump and the proportional speed control valve.

[0020] Secondly, this utility model also provides a tunnel boring machine, including the aforementioned tunnel boring machine hydraulic propulsion system.

[0021] This utility model has the following beneficial effects:

[0022] The shield machine hydraulic propulsion system provided by this utility model includes a proportional speed control valve and a proportional pressure reducing valve in the active control oil circuit to regulate the propulsion speed and propulsion pressure of the first cylinder, respectively. A pilot pressure reducing valve in the follower control oil circuit regulates the propulsion speed and propulsion pressure of the second cylinder. The control oil pressure, regulated by the proportional speed control valve and the proportional pressure reducing valve, controls the control terminal of the pilot pressure reducing valve. The working principle of the pilot pressure reducing valve is as follows: when the load pressure of the second cylinder is less than the load pressure of the first cylinder, the outlet pressure of the pilot pressure reducing valve is less than the control oil pressure. At this time, the opening of the pilot pressure reducing valve can be expanded by controlling the control oil pressure, thereby automatically increasing the propulsion pressure of the second cylinder to match that of the first cylinder. Conversely, when the load pressure of the second cylinder is greater than the load pressure of the first cylinder, the outlet pressure of the pilot pressure reducing valve is greater than the control oil pressure. At this time, the opening of the pilot pressure reducing valve can be reduced by controlling its outlet pressure, thereby automatically reducing the propulsion pressure of the second cylinder to match that of the first cylinder. The first cylinder's speed should be kept consistent with the first cylinder's speed. Similarly, when the second cylinder's speed is less than the first cylinder's speed, the second cylinder's load pressure will also be less than the first cylinder's load pressure. In this case, the pilot pressure reducing valve can automatically increase the second cylinder's speed to keep it consistent with the first cylinder's speed. Conversely, when the second cylinder's speed is greater than the first cylinder's speed, the second cylinder's load pressure will also be greater than the first cylinder's load pressure. In this case, the pilot pressure reducing valve can automatically decrease the second cylinder's speed to keep it consistent with the first cylinder's speed. Therefore, the proportional speed control valve and proportional pressure reducing valve in the hydraulic propulsion system of this tunnel boring machine only need to actively control the propulsion speed and pressure of the first cylinder. The use of small-flow proportional speed control valves and proportional pressure reducing valves can meet the requirements. The structure is simple and the cost is low, with a low failure rate. Furthermore, the follow-up control oil circuit enables the second cylinder to follow the first cylinder in propulsion pressure and propulsion speed through the pilot pressure reducing valve. This reduces the number of proportional speed control valves and proportional pressure reducing valves used, reduces the dependence on the size of the proportional speed control valves and proportional pressure reducing valves, and also enhances adaptability. It further simplifies the structure and reduces costs, and can ensure the coordination of different propulsion cylinders during the propulsion extension process.

[0023] 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

[0024] 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:

[0025] Figure 1A schematic diagram of the hydraulic propulsion system for a tunnel boring machine provided in this embodiment of the present invention.

[0026] Legend:

[0027] 1000. Shield machine hydraulic propulsion system;

[0028] 100. Active control oil circuit; 101. Proportional speed control valve; 102. Proportional pressure reducing valve; 103. First ball valve; 104. Pressure sensor; 105. Third check valve; 106. Third ball valve;

[0029] 200. Follow-up control oil circuit; 201. Second ball valve; 202. Pilot pressure reducing valve; 203. Fourth check valve;

[0030] 300. Propulsion cylinder; 301. First cylinder; 302. Second cylinder;

[0031] 1. First two-way cartridge valve; 2. First solenoid directional valve; 3. Second two-way cartridge valve; 4. Second solenoid directional valve; 5. Control branch; 51. First check valve; 52. Second check valve; 6. Third solenoid directional valve; 7. Third two-way cartridge valve; 8. Fourth two-way cartridge valve; 9. Safety valve. Detailed Implementation

[0032] 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. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0033] Those skilled in the art will understand that, unless specifically stated otherwise, the term "comprising" as used in this specification means the presence of the stated features, integers, steps, operations, components, and / or components, but does not exclude the presence or addition of one or more other features, integers, steps, operations, components, components, and / or combinations thereof. It should be understood that when we say a component is "connected" to another component, it can be directly connected to the other component or connected via an intermediate component. The term "and / or" as used herein includes all or any unit and all combinations of one or more associated listed items. The terms "first" and "second," etc., in this specification and claims are used to distinguish different objects, not to describe a particular order.

[0034] like Figure 1As shown, this utility model embodiment provides a shield machine hydraulic propulsion system 1000 for controlling multiple propulsion cylinders 300. The multiple propulsion cylinders 300 are respectively designated as a first cylinder 301 and a second cylinder 302. The shield machine hydraulic propulsion system 1000 includes an active control oil circuit 100 and a follower control oil circuit 200. The active control oil circuit 100 is used to connect to and control the first cylinder 301, and the follower control oil circuit 200 is used to connect to and control the second cylinder 302.

[0035] Preferably, the active control oil circuit 100 includes a first propulsion oil circuit disposed between the hydraulic pump and the rodless chamber of the first cylinder 301. The first propulsion oil circuit includes a proportional speed control valve 101, a proportional pressure reducing valve 102, and a first ball valve 103 arranged sequentially. The proportional speed control valve 101 is used to control the propulsion speed of the first cylinder 301, the proportional pressure reducing valve 102 is used to control the propulsion pressure of the first cylinder 301, and the first ball valve 103 is used to control the opening and closing of the oil circuit between the proportional pressure reducing valve 102 and the rodless chamber of the first cylinder 301. The follow control oil circuit 200 includes a first propulsion oil circuit disposed between the hydraulic pump and the rodless chamber of the first cylinder 301. The second propulsion oil passage between the rodless chamber of the second cylinder 302 includes a second ball valve 201 and a pilot pressure reducing valve 202 arranged in sequence. The second ball valve 201 is used to control the opening and closing of the oil passage between the pilot pressure reducing valve 202 and the rodless chamber of the second cylinder 302. The control end of the pilot pressure reducing valve 202 is connected to the output end of the proportional pressure reducing valve 102. That is, the pilot pressure reducing valve 202 is controlled by the control oil pressure adjusted by the proportional speed regulating valve 101 and the proportional pressure reducing valve 102, so that the propulsion pressure and propulsion speed of the second propulsion oil passage are consistent with those of the first propulsion oil passage.

[0036] Specifically, the shield machine hydraulic propulsion system 1000 is equipped with a proportional speed regulating valve 101 and a proportional pressure reducing valve 102 in the active control oil circuit 100 to adjust the propulsion speed and propulsion pressure of the first oil cylinder 301 respectively, and a pilot pressure reducing valve 202 is equipped in the follow control oil circuit 200 to adjust the propulsion speed and propulsion pressure of the second oil cylinder 302. The control terminal of the pilot pressure reducing valve 202 is controlled by the control oil pressure adjusted by the proportional speed regulating valve 101 and the proportional pressure reducing valve 102. The pilot pressure reducing valve 202 works as follows: When the load pressure of the second cylinder 302 is less than the load pressure of the first cylinder 301, the outlet pressure of the pilot pressure reducing valve 202 is less than the control oil pressure. At this time, the opening of the pilot pressure reducing valve 202 can be expanded by controlling the control oil pressure, thereby automatically increasing the pushing pressure of the second cylinder 302 to match that of the first cylinder 301. Conversely, when the load pressure of the second cylinder 302 is greater than the load pressure of the first cylinder 301, the outlet pressure of the pilot pressure reducing valve 202 is greater than the control oil pressure. At this time, the opening of the pilot pressure reducing valve 202 can be reduced by controlling its outlet pressure, thereby automatically reducing the pushing pressure of the second cylinder 302 to match that of the first cylinder 301. 1. To maintain consistency; similarly, when the pushing speed of the second cylinder 302 is less than the pushing speed of the first cylinder 301, the load pressure of the second cylinder 302 will also be less than the load pressure of the first cylinder 301. At this time, the pushing pressure of the second cylinder 302 can be automatically increased through the pilot pressure reducing valve 202 to keep the pushing speed of the second cylinder 302 consistent with that of the first cylinder 301; while when the pushing speed of the second cylinder 302 is greater than the pushing speed of the first cylinder 301, the load pressure of the second cylinder 302 will also be greater than that of the first cylinder 301. At this time, the pushing pressure of the second cylinder 302 can be automatically reduced through the pilot pressure reducing valve 202 to keep the pushing speed of the second cylinder 302 consistent with that of the first cylinder 301. Therefore, the proportional speed control valve 101 and proportional pressure reducing valve 102 in the shield machine hydraulic propulsion system 1000 only need to actively control the propulsion speed and propulsion pressure of the first cylinder 301. The use of small-flow proportional speed control valve 101 and proportional pressure reducing valve 102 can meet the usage requirements. The structure is simple, the cost is low, and the failure rate is low. Furthermore, the follow control oil circuit 200 realizes the second cylinder 302 following the first cylinder 301 in propulsion pressure and propulsion speed through the pilot pressure reducing valve 202. This reduces the number of proportional speed control valves 101 and proportional pressure reducing valves 102 used, reduces the dependence on the size of the proportional speed control valves 101 and proportional pressure reducing valves 102, and also enhances adaptability. It further simplifies the structure and reduces costs, and can ensure the coordination of different propulsion cylinders 300 during the propulsion extension process.

[0037] It is worth noting that this embodiment of the present invention uses one second hydraulic cylinder 302 and one follower control oil circuit 200 as an example to illustrate the working principle of the shield machine hydraulic propulsion system 1000, but it should not be regarded as a limitation on the specific number of the second hydraulic cylinder 302 and the follower control oil circuit 200. In actual applications, there may be multiple second hydraulic cylinders 302 and multiple follower control oil circuits 200. The multiple follower control oil circuits 200 are connected one-to-one with the rodless chambers of the multiple second hydraulic cylinders 302, so that the multiple second hydraulic cylinders 302 can follow the first hydraulic cylinder 301 to achieve the following of the propulsion pressure and propulsion speed.

[0038] Preferably, both the active control oil circuit 100 and the follower control oil circuit 200 include a first two-way cartridge valve 1 and a first solenoid directional valve 2. The first solenoid directional valve 2 is connected to the control end of the first two-way cartridge valve 1 and is used to control the opening and closing of the first two-way cartridge valve 1. The first two-way cartridge valve 1 in the active control oil circuit 100 is used to connect the hydraulic pump to the rodless chamber of the first cylinder 301, thereby controlling the oil intake of the rodless chamber of the first cylinder 301. The first two-way cartridge valve 1 in the follower control oil circuit 200 is used to connect the hydraulic pump to the rodless chamber of the second cylinder 302, thereby controlling the oil intake of the rodless chamber of the second cylinder 302.

[0039] It should be understood that the tunnel boring machine has a propulsion mode and an assembly mode. In propulsion mode, the shield propels the machine on the pre-assembled tunnel segments. This requires precise excavation and places high demands on the propulsion speed and pressure of the propulsion cylinder 300. This can be precisely controlled through the first and second propulsion oil circuits. In assembly mode, the tunnel segments are assembled. This does not require excavation and the propulsion cylinder 300 needs to complete the action at a faster speed. Therefore, the first two-way cartridge valve 1 can be opened by controlling the first electromagnetic reversing valve 2, thereby directly connecting the rodless chambers of the first cylinder 301 and the second cylinder 302 to the hydraulic pump. The hydraulic pump directly controls the piston rod extension of the propulsion cylinder 300, meeting the rapid action requirements of the assembly mode and improving efficiency.

[0040] Preferably, both the active control oil circuit 100 and the follower control oil circuit 200 include a second two-way cartridge valve 3 and a second solenoid directional valve 4. The second solenoid directional valve 4 is connected to the control end of the second two-way cartridge valve 3 and is used to control the opening and closing of the second two-way cartridge valve 3. The second two-way cartridge valve 3 in the active control oil circuit 100 is used to connect the oil tank and the rodless chamber of the first cylinder 301 to control the return oil from the rodless chamber of the first cylinder 301. The second two-way cartridge valve 3 in the follower control oil circuit 200 is used to connect the oil tank and the rodless chamber of the second cylinder 302 to control the return oil from the rodless chamber of the second cylinder 302.

[0041] Similarly, the cooperation of the second two-way cartridge valve 3 and the second solenoid directional valve 4 enables rapid connection between the rodless chamber of the propulsion cylinder 300 and the oil tank, thereby achieving rapid pressure relief and oil return to the rodless chambers of the first cylinder 301 and the second cylinder 302, meeting the rapid operation requirements of the tunnel boring machine in assembly mode. Furthermore, the rapid oil inlet and return lines of the rodless chamber of the propulsion cylinder 300 are controlled by independent two-way cartridge valves and solenoid directional valves. This not only allows for separate control of the oil inlet and return actions but also enables the simultaneous closure of the first two-way cartridge valve 1 and the second two-way cartridge valve 3 after the piston rod of the propulsion cylinder 300 extends, achieving pressure holding in the rodless chamber and meeting different operational requirements of the tunnel boring machine.

[0042] More preferably, both the active control oil circuit 100 and the follower control oil circuit 200 include a control branch 5. The first end of the control branch 5 is provided with a first check valve 51 for connection to a hydraulic pump, and the second end of the control branch 5 is provided with a second check valve 52 for connection to the rodless chamber of the corresponding propulsion cylinder 300. The control ends of the first solenoid directional valve 2 and the second solenoid directional valve 4 located in the same control oil circuit are arranged in parallel and are both connected to the third end of the control branch 5. The hydraulic direction of the first check valve 51 and the second check valve 52 is both oriented towards the third end of the control branch 5.

[0043] Specifically, in the active control oil circuit 100, the first end of the control branch 5 is provided with a first check valve 51 for connection to the hydraulic pump, and the second end of the control branch 5 is provided with a second check valve 52 for connection to the rodless chamber of the first cylinder 301. The control ends of the first solenoid directional valve 2 and the second solenoid directional valve 4 in the active control oil circuit 100 are connected in parallel and are both connected to the third end of the control branch 5 in the active control oil circuit 100. Similarly, in the follower control oil circuit 200, the first end of the control branch 5 is provided with a first check valve 51 for connection to the hydraulic pump, and the second end of the control branch 5 is provided with a second check valve 52 for connection to the rodless chamber of the second cylinder 302. The control ends of the first solenoid directional valve 2 and the second solenoid directional valve 4 in the follower control oil circuit 200 are connected in parallel and are both connected to the third end of the control branch 5 in the follower control oil circuit 200. This allows the higher pressure of the hydraulic pump's output pressure and the rodless chamber pressure of the propulsion cylinder 300 to be used as the control pressure for the first solenoid directional valve 2 and the second solenoid directional valve 4. When the hydraulic pump is running, the first solenoid directional valve 2 and the second solenoid directional valve 4 can be flexibly controlled by the hydraulic pump's output pressure. When the hydraulic pump is temporarily stopped and the rodless chamber of the propulsion cylinder 300 is in a pressure-holding state, the first solenoid directional valve 2 and the second solenoid directional valve 4 can still be controlled by the rodless chamber pressure of the propulsion cylinder 300. This avoids sudden shutdown that could cause the first solenoid directional valve 2 and the second solenoid directional valve 4 to lose power, thereby preventing the rodless chamber of the propulsion cylinder 300 from suddenly depressurizing due to the hydraulic pump's shutdown.

[0044] Preferably, both the active control oil circuit 100 and the follower control oil circuit 200 include a third solenoid directional valve 6, and a third two-way cartridge valve 7 and a fourth two-way cartridge valve 8 respectively connected to the third solenoid directional valve 6. The third solenoid directional valve 6 is used to switchably control one of the third two-way cartridge valve 7 and the fourth two-way cartridge valve 8 to be open and the other to be closed, that is, when the third two-way cartridge valve 7 is open, the fourth two-way cartridge valve 8 is closed; when the third two-way cartridge valve 7 is closed, the fourth two-way cartridge valve 8 is open.

[0045] Furthermore, the third two-way cartridge valve 7 of the active control oil circuit 100 is used to be installed between the hydraulic pump and the rod chamber of the first cylinder 301, the fourth two-way cartridge valve 8 of the active control oil circuit 100 is used to be installed between the oil tank and the rod chamber of the first cylinder 301, the third two-way cartridge valve 7 of the follow control oil circuit 200 is used to be installed between the hydraulic pump and the rod chamber of the second cylinder 302, and the fourth two-way cartridge valve 8 of the follow control oil circuit 200 is used to be installed between the oil tank and the rod chamber of the second cylinder 302.

[0046] Since the rod chamber of the propulsion cylinder 300 does not require pressure holding, the switching between oil inlet and oil return actions of the rod chamber of the propulsion cylinder 300 can be realized by simultaneously controlling the opening and closing of the third two-way cartridge valve 7 and the fourth two-way cartridge valve 8 through a third solenoid directional valve 6. The control structure is simple and efficient, and can realize rapid oil inlet or rapid oil return of the rod chambers of the first cylinder 301 and the second cylinder 302.

[0047] Preferably, both the active control oil circuit 100 and the follower control oil circuit 200 include a safety valve 9. The safety valve 9 is disposed between the rod chamber of the corresponding propulsion cylinder 300 and the oil tank. Specifically, the safety valve 9 in the active control oil circuit 100 is disposed between the rod chamber of the first cylinder 301 and the oil tank, and the safety valve 9 in the follower control oil circuit 200 is disposed between the rod chamber of the second cylinder 302 and the oil tank. The safety valve 9 is normally closed and is used to open the oil tank to release pressure when the pressure in the rod chamber of the corresponding propulsion cylinder 300 exceeds a preset value, thereby limiting the maximum pressure in the rod chambers of the first cylinder 301 and the second cylinder 302, respectively, thus providing safety protection.

[0048] Preferably, the active control oil circuit 100 further includes a pressure sensor 104 for connecting to the rodless chamber of the first oil cylinder 301. The pressure sensor 104 is used to monitor the pressure of the rodless chamber of the first oil cylinder 301 in real time to avoid abnormal pressure in the rodless chamber of the first oil cylinder 301. Since the pressure of the rodless chamber of the second oil cylinder 302 can automatically follow the pressure of the rodless chamber of the first oil cylinder 301, by monitoring the pressure of the rodless chamber of the first oil cylinder 301, the pressure of the rodless chamber of all propulsion cylinders 300 can be known at the same time, without the need to configure multiple pressure sensors 104, making the monitoring structure simple and efficient.

[0049] Furthermore, the active control oil circuit 100 also includes a third check valve 105 disposed between the first ball valve 103 and the rodless chamber of the first cylinder 301, and the follow control oil circuit 200 also includes a fourth check valve 203 disposed between the pilot pressure reducing valve 202 and the rodless chamber of the second cylinder 302. The third check valve 105 and the fourth check valve 203 respectively maintain pressure in the rodless chambers of the first cylinder 301 and the second cylinder 302, preventing pressure loss in the rodless chamber of the propulsion cylinder 300 along the first propulsion oil circuit or the second propulsion oil circuit.

[0050] Furthermore, the active control oil circuit 100 also includes a third ball valve 106 disposed between the hydraulic pump and the proportional speed control valve 101, which controls the opening and closing of the oil circuit to enable control of multiple propulsion cylinders 300.

[0051] Secondly, this utility model embodiment also provides a tunnel boring machine (not shown in the figure, the same below), including the above-mentioned tunnel boring machine hydraulic propulsion system 1000. Since the tunnel boring machine hydraulic propulsion system 1000 can realize the follow-up action of the propulsion pressure and propulsion speed of multiple propulsion cylinders 300, it eliminates the need for multiple proportional speed control valves 101 and multiple proportional pressure reducing valves 102, and has lower flow requirements for the proportional speed control valves 101 and the proportional pressure reducing valves 102. This greatly simplifies the hydraulic control system, meets propulsion requirements, facilitates the miniaturization of the tunnel boring machine, and reduces the cost and failure rate of the tunnel boring machine.

[0052] 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 propulsion system for a tunnel boring machine, used to control multiple propulsion cylinders (300), wherein the multiple propulsion cylinders (300) are respectively designated as a first cylinder (301) and a second cylinder (302), characterized in that, The shield machine hydraulic propulsion system includes an active control circuit (100) for connection to the first cylinder (301) and a follower control circuit (200) for connection to the second cylinder (302); The active control oil circuit (100) includes a first propulsion oil circuit disposed between the hydraulic pump and the rodless chamber of the first cylinder (301). The first propulsion oil circuit includes a proportional speed control valve (101), a proportional pressure reducing valve (102), and a first ball valve (103) disposed in sequence. The proportional speed control valve (101) is used to control the propulsion speed of the first cylinder (301), and the proportional pressure reducing valve (102) is used to control the propulsion pressure of the first cylinder (301). The following control oil circuit (200) includes a second propulsion oil circuit disposed between the hydraulic pump and the rodless chamber of the second cylinder (302). The second propulsion oil circuit includes a second ball valve (201) and a pilot pressure reducing valve (202) disposed in sequence. The control end of the pilot pressure reducing valve (202) is connected to the output end of the proportional pressure reducing valve (102) so that the propulsion pressure and propulsion speed of the second propulsion oil circuit are consistent with those of the first propulsion oil circuit.

2. The shield machine hydraulic propulsion system according to claim 1, characterized in that, The active control oil circuit (100) and the follower control oil circuit (200) both include a first two-way cartridge valve (1) and a first solenoid directional valve (2). The first solenoid directional valve (2) is connected to the control end of the first two-way cartridge valve (1) and is used to control the opening and closing of the first two-way cartridge valve (1). The first two-way cartridge valve (1) in the active control oil circuit (100) is used to connect the hydraulic pump to the rodless chamber of the first cylinder (301) to control the oil intake of the rodless chamber of the first cylinder (301). The first two-way cartridge valve (1) in the follow control oil circuit (200) is used to connect the hydraulic pump to the rodless chamber of the second cylinder (302) to control the oil intake of the rodless chamber of the second cylinder (302).

3. The shield machine hydraulic propulsion system according to claim 2, characterized in that, Both the active control oil circuit (100) and the follower control oil circuit (200) include a second two-way cartridge valve (3) and a second solenoid directional valve (4). The second solenoid directional valve (4) is connected to the control end of the second two-way cartridge valve (3) and is used to control the opening and closing of the second two-way cartridge valve (3). The second two-way cartridge valve (3) in the active control oil circuit (100) is used to connect the oil tank and the rodless chamber of the first oil cylinder (301) to control the return oil of the rodless chamber of the first oil cylinder (301). The second two-way cartridge valve (3) in the follow control oil circuit (200) is used to connect the oil tank and the rodless chamber of the second oil cylinder (302) to control the return oil of the rodless chamber of the second oil cylinder (302).

4. The shield machine hydraulic propulsion system according to claim 3, characterized in that, Both the active control circuit (100) and the follower control circuit (200) include a control branch (5). The first end of the control branch (5) is provided with a first check valve (51) for connection to a hydraulic pump. The second end of the control branch (5) is provided with a second check valve (52) for connection to the rodless chamber of the corresponding propulsion cylinder (300). The control ends of the first solenoid directional valve (2) and the second solenoid directional valve (4) located in the same control circuit are connected in parallel and are both connected to the third end of the control branch (5). The hydraulic direction of the first check valve (51) and the second check valve (52) is both directed toward the third end of the control branch (5).

5. The shield machine hydraulic propulsion system according to claim 1, characterized in that, Both the active control circuit (100) and the follower control circuit (200) include a third solenoid directional valve (6), and a third two-way cartridge valve (7) and a fourth two-way cartridge valve (8) respectively connected to the third solenoid directional valve (6). The third solenoid directional valve (6) is used to switchably control one of the third two-way cartridge valve (7) and the fourth two-way cartridge valve (8) to be open and the other to be closed. The third two-way cartridge valve (7) of the active control circuit (100) is used to be installed between the hydraulic pump and the rod chamber of the first cylinder (301). The fourth two-way cartridge valve (8) of the active control circuit (100) is used to be installed between the oil tank and the rod chamber of the first cylinder (301). The third two-way cartridge valve (7) of the follow control circuit (200) is used to be installed between the hydraulic pump and the rod chamber of the second cylinder (302). The fourth two-way cartridge valve (8) of the follow control circuit (200) is used to be installed between the oil tank and the rod chamber of the second cylinder (302).

6. The shield machine hydraulic propulsion system according to claim 1, characterized in that, Both the active control oil circuit (100) and the follow control oil circuit (200) include a safety valve (9), which is used to be installed between the rod chamber of the corresponding propulsion cylinder (300) and the oil tank.

7. The shield machine hydraulic propulsion system according to claim 1, characterized in that, The active control circuit (100) also includes a pressure sensor (104) for connection to the rodless chamber of the first cylinder (301).

8. The shield machine hydraulic propulsion system according to claim 1, characterized in that, The active control circuit (100) further includes a third check valve (105) disposed between the first ball valve (103) and the rodless chamber of the first cylinder (301), and the follow control circuit (200) further includes a fourth check valve (203) disposed between the pilot pressure reducing valve (202) and the rodless chamber of the second cylinder (302).

9. The shield machine hydraulic propulsion system according to claim 1, characterized in that, The active control circuit (100) also includes a third ball valve (106) for use between the hydraulic pump and the proportional speed control valve (101).

10. A tunnel boring machine, characterized in that, Includes the shield machine hydraulic propulsion system as described in any one of claims 1 to 9.

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