Rotary hydraulic control device of shield segment machine

Abstract

The rotary hydraulic control device of the shield segment machine comprises a hydraulic control valve bank, a motor control valve bank and a motor driving mechanism, the motor control valve bank is connected with the motor driving mechanism to control the motor driving mechanism to act, and the hydraulic control valve bank and the motor driving mechanism are used for controlling the motor driving mechanism to brake. The hydraulic control valve set is connected with the motor control valve set at the same time to control the motor control valve set, the motor control valve set comprises a large-flow hydraulic lock, a bidirectional overflow valve and a small-flow balance valve, and the small-flow balance valve and the bidirectional overflow valve are sequentially connected between the hydraulic control valve set and the motor driving mechanism in series. And the large-flow hydraulic lock is connected in parallel with a bypass of the small-flow balance valve and the bidirectional overflow valve and is connected with the hydraulic control valve group and the motor driving mechanism. The proportional servo valve is matched with the small-flow balance valve and is connected in parallel with the large-flow hydraulic lock to control the position of the duct piece; therefore, the phenomenon that shaking is easy to generate when a proportional valve is matched with a high-flow balance valve to position the duct piece is improved.

Description

Technical Field

[0001] This utility model belongs to the field of shield tunnel segment machine control technology, specifically relating to a shield tunnel segment machine rotation hydraulic control device. Background Technology

[0002] Currently, most actions in the hydraulic system of tunnel segment machines are manually controlled. The pump station is directly connected to a set of manual multi-way valves to control the forward, backward, and rotation of the segments. The positional accuracy of the segments can only be controlled by the worker's feel and skill. To solve the problem of poor control accuracy, proportional valves were used to replace the original multi-way valves. The proportional valves were installed on the hydraulic control valve group and controlled by the PLC through commands to open and close them. Although this solved the problem of poor positioning of segments by manual placement, at the same time, due to the small flow rate of the liquid in the pipeline, the large diameter of the high-flow balance valve caused an imbalance between the proportional valve and the high-flow balance valve. When the small flow rate of liquid passes through, the high-flow balance valve opens and closes frequently in a short period of time, which makes the segments prone to shaking during positioning. Utility Model Content

[0003] To address the aforementioned technical problems, the present invention aims to provide a rotating hydraulic control device for tunnel segment machines. This device uses a proportional servo valve in conjunction with a small-flow balance valve and a large-flow hydraulic lock in parallel to control the segment position. During long strokes, a large-flow hydraulic lock is used for direct control, while for precise positioning, a small-flow servo proportional valve in conjunction with a small-flow balance valve is used for accurate positioning. This avoids the problem of vibration that easily occurs when using a proportional valve in conjunction with a large-flow balance valve to position the segments.

[0004] To achieve the above objectives, the technical solution adopted by this utility model is as follows:

[0005] A rotating hydraulic control device for a tunnel boring machine (TBM) includes a hydraulic control valve group, a motor control valve group, and a motor drive mechanism. The motor control valve group is connected to the motor drive mechanism, and the hydraulic control valve group is also connected to the motor drive mechanism. The motor control valve group includes a high-flow hydraulic lock, a two-way relief valve, and a low-flow balancing valve. The low-flow balancing valve and the two-way relief valve are connected in series between the hydraulic control valve group and the motor drive mechanism. The high-flow hydraulic lock is connected in parallel to the bypass of the low-flow balancing valve and the two-way relief valve, and is connected to the hydraulic control valve group and the motor drive mechanism.

[0006] Furthermore, the hydraulic control valve group includes a first solenoid valve, a second solenoid valve, and a proportional servo valve. The first solenoid valve, the proportional servo valve, and the second solenoid valve are connected in parallel at one end. The other end of the first solenoid valve is connected to a high-flow hydraulic lock. The other end of the proportional servo valve is connected in parallel to a low-flow balance valve and a high-flow hydraulic lock. The other end of the second solenoid valve is connected to a motor drive mechanism.

[0007] Furthermore, the high-flow hydraulic lock includes a first pilot port, a second pilot port, a first channel, and a second channel. One end of the first pilot port and one end of the second pilot port are connected in parallel to the hydraulic control valve assembly. The other end of the first pilot port is connected to the first channel, and the other end of the second pilot port is connected to the second channel. One end of the first channel and one end of the second channel are both connected in parallel to one end of the bidirectional relief valve and then connected to the motor drive mechanism. The other end of the first channel and the other end of the second channel are both connected in parallel to one end of the low-flow balance valve and then connected to the hydraulic control valve assembly.

[0008] Furthermore, one end of the first pilot port and one end of the second pilot port are connected in parallel to the first solenoid valve, and one end of the small flow balancing valve is connected to the proportional servo valve.

[0009] Furthermore, the motor drive mechanism includes a hydraulic motor, a tube sheet machine gear ring rotating component, and a locking component. The hydraulic motor is connected to the tube sheet machine gear ring rotating component, the locking component is coaxially connected to the hydraulic motor, and one end of the locking component is connected to a hydraulic control valve group.

[0010] Furthermore, the proportional servo valve is a high-response dynamic proportional servo valve.

[0011] Furthermore, both the first and second solenoid valves are 2-position 4-way solenoid valves.

[0012] By adopting the above technical solution, this utility model has the following advantages and effects:

[0013] (1) The present invention provides a rotating hydraulic control device for a tunnel segment machine, which has a set of high-flow hydraulic locks connected in parallel next to a low-flow balance valve. When the segment machine performs a rotating action, it can quickly transport the segment to the required position and lock the oil passage during precise positioning to prevent interference.

[0014] (2) Existing proportional servo valves use linear proportional valve cores, and the signal and flow are adjusted proportionally. When adjusting large flow rates (30% to 310% flow rate), it is relatively easy to adjust. However, when adjusting small flow rates (0% to 31% flow rate), it is not possible to control the flow output in this range more accurately. This utility model adopts a high-response dynamic proportional servo valve, which can provide the large flow rate of oil required by the device (6-31v can provide 31% to 310% flow rate) and can also provide precise speed control at small flow rates (6-31v can provide 1% to 31% flow rate), thereby enabling the tube segment to be accurately positioned and avoiding vibration. Attached Figure Description

[0015] Figure 1 This is a schematic diagram of the structure of this utility model.

[0016] Figure 2 This is a diagram showing the signal flow regulation ratio of a proportional servo valve.

[0017] The attached figures are labeled as follows: 1-Hydraulic control valve group, 11-First solenoid valve, 12-Proportional servo valve, 13-Second solenoid valve, 2-Motor control valve group, 21-High-flow hydraulic lock, 22-Two-way relief valve, 23-Small-flow balance valve, 3-Motor drive mechanism, 31-Segmentation machine gear ring rotating component, 32-Hydraulic motor, 33-Locking component. Detailed Implementation

[0018] The embodiments of this utility model will be described in detail below with reference to the accompanying drawings, so as to better understand the purpose, features and advantages of this utility model. It should be understood that the embodiments shown in the drawings are not intended to limit the scope of this utility model, but are only for illustrating the essential spirit of the technical solution of this utility model.

[0019] like Figure 1 As shown. This utility model discloses a rotating hydraulic control device for a tunnel boring machine (TBM), comprising a hydraulic control valve group 1, a motor control valve group 2, and a motor drive mechanism 3. The motor control valve group 2 is connected to the motor drive mechanism 3. The hydraulic control valve group 1 is connected to the motor control valve group 2 to control the operation of the motor drive mechanism 3. The hydraulic control valve group 1 is also connected to the motor drive mechanism 3 to control the braking of the motor drive mechanism 3. The motor control valve group 2 includes a high-flow hydraulic lock 21, a two-way relief valve 22, and a low-flow balance valve 23. The low-flow balance valve 23 and the two-way relief valve 22 are connected in series between the hydraulic control valve group 1 and the motor drive mechanism 3. The high-flow hydraulic lock 21 is connected in parallel to the bypass of the low-flow balance valve 23 and the two-way relief valve 22, and is connected to the hydraulic control valve group 1 and the motor drive mechanism 3.

[0020] Specifically, the motor control valve group 2 also includes a first external interface X1, a first external oil port A5, a second external oil port B5, a third external oil port A6, a fourth external oil port B6, a fifth external oil port A7, and a sixth external oil port B7. The first external oil port A5, the second external oil port B5, and the first external interface X1 connect one end of the high-flow hydraulic lock 21 to the hydraulic control valve group 1. The third external oil port A6 and the fourth external oil port B6 connect one end of the low-flow balance valve 23 to the hydraulic control valve group 1. The fifth external oil port A7 and the sixth external oil port B7 connect the other end of the high-flow hydraulic lock 21, one end of the bidirectional relief valve 22, and the motor drive mechanism 3.

[0021] Furthermore, the high-flow hydraulic lock 21 includes a first pilot port Y5, a second pilot port Y6, a first channel, and a second channel. One end of the first pilot port Y5 and one end of the second pilot port Y6 are connected in parallel to the hydraulic control valve group 1. The other end of the first pilot port Y5 is connected to the first channel, and the other end of the second pilot port Y6 is connected to the second channel. One end of the first channel and one end of the second channel are both connected in parallel to one end of the bidirectional relief valve 22 and then connected to the motor drive mechanism 3. The other end of the first channel and the other end of the second channel are both connected in parallel to one end of the low-flow balance valve 23 and then connected to the hydraulic control valve group 1.

[0022] Specifically, the high-flow hydraulic lock 21 also includes a first port Y1, a second port Y2, a third port Y3, and a fourth port Y4. The first port Y1 and the third port Y3 form a first channel, and the second port Y2 and the fourth port Y4 form a second channel. One end of the first pilot port Y5 is connected to one end of the check valve in the middle of the first channel, and one end of the second pilot port Y6 is connected to one end of the check valve in the middle of the second channel. The first pilot port Y5 and the second pilot port Y6 are connected in parallel to the first external interface X1, which is connected to the hydraulic control valve group 1. The fourth port Y4 is connected to the fifth external oil port A7, the third port Y3 is connected to the sixth external oil port B7, the first port Y1 is connected to the second external oil port B5, and the second port Y2 is connected to the first external oil port A5. When the first pilot port Y5 and the second pilot port Y6 are in passage, the high-flow hydraulic lock 21 can flow from the third port Y3 to the first port Y1 or from the fourth port Y4 to the second port Y2 in reverse. If the first pilot port Y5 and the second pilot port Y6 are disconnected, the high-flow hydraulic lock 21 can only flow from the first port Y1 to the third port Y3 or from the second port Y2 to the fourth port Y4, and cannot flow in reverse.

[0023] The bidirectional relief valve 22 includes a first oil passage and a second oil passage. The two ends of the first oil passage are a first interface M1 and a third interface M3, respectively. The two ends of the second oil passage are a second interface M2 and a fourth interface M4, respectively. The first interface M1 and the second interface M2 are connected to the small flow balance valve 23. The third interface M3 is connected in parallel with one end of the second channel of the large flow hydraulic lock 21 and then connected to the fifth external oil port A7. The fourth interface M4 is connected in parallel with one end of the first channel of the large flow hydraulic lock 21 and then connected to the sixth external oil port B7.

[0024] When the pressure in the first oil passage exceeds the preset pressure value, the oil in the first oil passage flows into the second oil passage. When the pressure in the second oil passage exceeds the preset pressure value, the oil in the second oil passage flows into the first oil passage to achieve mutual pressure relief.

[0025] The small-flow balancing valve 23 includes a one-way oil passage and a balancing oil passage. The two ends of the one-way oil passage are the oil inlet N1 and the oil outlet N3, respectively. The two ends of the balancing oil passage are the oil outlet inlet N4 and the oil outlet N2, respectively. The oil inlet N1 and the oil outlet N2 are connected to the hydraulic control valve group 1 through the third external oil port A6 and the fourth external oil port B6. The oil outlet N3 is connected to the first port M1 of the two-way relief valve 22, and the oil outlet N4 is connected to the second port M2 of the two-way relief valve 22. A check valve is connected in series on the oil inlet N1 and the oil outlet N3, which can realize the one-way flow of oil from the oil inlet N1 through the check valve to the oil outlet N3. A check valve is connected in series between the oil outlet inlet N4 and the oil outlet outlet N2. Because the small-flow balance valve 23 has a certain pressure, the check valve can only open when the return oil pressure reaches the set value. The return oil enters the small-flow balance valve 23 from the oil outlet inlet N4 and flows directly out from the oil outlet outlet N2 without passing through the check valve. One end of the oil inlet N1 is connected to the hydraulic control valve group 1 via the third external port A6. One end of the oil outlet outlet N2 is connected to the hydraulic control valve group 1 via the fourth external port B6.

[0026] Furthermore, the hydraulic control valve assembly 1 includes a first solenoid valve 11, a second solenoid valve 13, and a proportional servo valve 12. One end of the first solenoid valve 11, the proportional servo valve 12, and the second solenoid valve 13 are connected in parallel. The other end of the first solenoid valve 11 is connected to a high-flow hydraulic lock 21. The other end of the proportional servo valve 12 is connected in parallel to a low-flow balance valve 23 and a high-flow hydraulic lock 21. The other end of the second solenoid valve 13 is connected to a motor drive mechanism 3. By adding the first solenoid valve 11 in series with the high-flow hydraulic lock 21, the motor drive mechanism 3 can be controlled in parallel, thus narrowing the flow range of the low-flow balance valve 23.

[0027] Specifically, the hydraulic control valve assembly 1 further includes a first hydraulic channel P, a second hydraulic channel T, a first oil outlet A1, a second oil outlet B1, a third oil outlet A2, a fourth oil outlet B2, a fifth oil outlet A3, a sixth oil outlet B3, a seventh oil outlet A4, and an eighth oil outlet B4. The oil outlet P1 of the first solenoid valve 11 is connected to the first hydraulic channel P, and the oil outlet T1 of the first solenoid valve 11 is connected to the second hydraulic channel T; the oil outlet B of the first solenoid valve 11 is connected to the second oil outlet B1, and the oil outlet A of the first solenoid valve 11 is connected to the first oil outlet A1, with the first oil outlet A1 closed.

[0028] Under normal conditions, oil ports T1 and B of the first solenoid valve 11 are connected, and oil ports A and P1 are connected. After being energized, oil ports A and T1 are connected, and oil ports B and P1 are connected.

[0029] The oil port P2 of the second solenoid valve 13 is connected to the first hydraulic channel P, and the oil port T2 of the second solenoid valve 13 is connected to the second hydraulic channel T. The oil port B0 of the second solenoid valve 13 is connected to the eighth oil outlet B4, which is connected to the motor drive mechanism 3. The oil port A0 of the second solenoid valve 13 is connected to the seventh oil outlet A4, and the seventh oil outlet A4 is closed. Under normal conditions, the oil ports T2 and B0 of the second solenoid valve 13 are connected, and the oil ports A0 and P2 are connected. When energized, the oil ports A0 and T2 are connected, and the oil ports B0 and P2 are connected.

[0030] Port P3 of the proportional servo valve 12 is connected to the first hydraulic channel P, and port T3 of the proportional servo valve 12 is connected to the second hydraulic channel T. Port A9 of the proportional servo valve 12 is connected in parallel to the third outlet A2 and the fifth outlet A3. The third outlet A2 is connected to the first external outlet A5 of the motor control valve group 2, and the fifth outlet A3 is connected to the third external outlet A6 of the motor control valve group 2.

[0031] The oil port B9 of the proportional servo valve 12 is connected in parallel to the fourth oil port B2 and the sixth oil port B3. The fourth oil port B2 is connected to the second external oil port B5 of the motor control valve group 2, and the sixth oil port B3 is connected to the fourth external oil port B6 of the motor control valve group 2.

[0032] Under normal conditions, ports T3 and B9 of the proportional servo valve 12 are connected, and ports A9 and P3 are connected. After being energized, ports A9 and T3 of the proportional servo valve 12 are connected, and ports B9 and P3 are connected.

[0033] Furthermore, the motor drive mechanism 3 includes a hydraulic motor 32, a tube sheet machine gear ring rotating component 31, and a locking component 33. The hydraulic motor 32 is connected to the tube sheet machine gear ring rotating component 31, and the locking component 33 is coaxially connected to the hydraulic motor 32. One end of the locking component 33 is connected to the hydraulic control valve group 1.

[0034] Specifically, the motor drive mechanism 3 also includes a second external interface A8, a third external interface B8, a first oil port L1, a second oil port L2, and a brake hydraulic port L3. The first oil port L1 and the second oil port L2 are located at opposite ends of the hydraulic motor 32 and are used to drive the hydraulic motor 32 to rotate forward and backward. The first oil port L1 is connected to the fifth external oil port A7 through the second external interface A8, and the second oil port L2 is connected to the sixth external oil port B7 through the third external interface B8. The locking member 33 is connected to the eighth oil outlet B4 of the hydraulic control valve group 1 through the brake hydraulic port L3 and then connected to the second solenoid valve 13. The second solenoid valve 13 controls the locking member 33 to brake the hydraulic motor 32. Since the hydraulic motor 32 drives the segmenter gear ring rotating member 31 to rotate and drive the segmenter segments, the hydraulic motor 32 can rotate freely when it is not working. Hydraulic power cannot lock the hydraulic motor 32. The locking member 33 is coaxially connected to the hydraulic motor 32 to lock the rotation of the hydraulic motor 32. The locking element 33 is preferably a hydraulically driven shoe brake, which locks the shaft through mechanical friction.

[0035] Furthermore, both the first solenoid valve 11 and the second solenoid valve 13 are 2-position 4-way solenoid valves. The proportional servo valve 12 is a high-response dynamic proportional servo valve, and the reference signal and the regulating flow ratio of the proportional servo valve 12 are, for example... Figure 2 As shown.

[0036] When this utility model is in use, firstly, after the tube sheet machine is given an operating command, and the tube sheet machine is required to run to a designated position, the second solenoid valve 13 is energized, the self-locking cylinder of the hydraulic motor 32 is opened, and then the first solenoid valve 11 is energized, the channel of the high-flow hydraulic lock 21 is opened, and the proportional servo valve 12 controls the forward and reverse rotation of the hydraulic motor 32 in the range of 6-31V.

[0037] Oil enters from the end of the first hydraulic channel P of the hydraulic control valve group 1, flows through the proportional servo valve 12, passes through the high-flow hydraulic lock 21, and enters the motor drive mechanism 3 to drive the hydraulic motor 32 to rotate forward and reverse, thereby realizing the rapid operation of the hydraulic motor 32.

[0038] When the hydraulic motor 32 rotates to the set area, the first solenoid valve 11 is de-energized, the first channel of the high-flow hydraulic lock 21 is closed, and the proportional servo valve 12 controls the fine-tuning part of the hydraulic motor 32 in the range of 0-6V to achieve precise positioning of the tunnel segment.

[0039] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this utility model, and not to limit it; although the utility model has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of this utility model.

Claims

1. A rotary hydraulic control device for a tunnel boring machine segment machine, characterized in that, The system includes a hydraulic control valve assembly, a motor control valve assembly, and a motor drive mechanism. The motor control valve assembly is connected to the motor drive mechanism, and the hydraulic control valve assembly is also connected to the motor drive mechanism. The motor control valve assembly includes a high-flow hydraulic lock, a two-way relief valve, and a low-flow balancing valve. The low-flow balancing valve and the two-way relief valve are connected in series between the hydraulic control valve assembly and the motor drive mechanism. The high-flow hydraulic lock is connected in parallel to the bypass of the low-flow balancing valve and the two-way relief valve, and is connected to the hydraulic control valve assembly and the motor drive mechanism.

2. The shield tunnel segment machine rotation hydraulic control device according to claim 1, characterized in that, The hydraulic control valve group includes a first solenoid valve, a second solenoid valve, and a proportional servo valve. The first solenoid valve, the proportional servo valve, and the second solenoid valve are connected in parallel at one end. The other end of the first solenoid valve is connected to a high-flow hydraulic lock. The other end of the proportional servo valve is connected in parallel to a low-flow balance valve and a high-flow hydraulic lock. The other end of the second solenoid valve is connected to a motor drive mechanism.

3. The shield tunnel segment machine rotation hydraulic control device according to claim 2, characterized in that, The high-flow hydraulic lock includes a first pilot port, a second pilot port, a first channel, and a second channel. One end of the first pilot port and one end of the second pilot port are connected in parallel to a hydraulic control valve assembly. The other end of the first pilot port is connected to the first channel, and the other end of the second pilot port is connected to the second channel. One end of the first channel and one end of the second channel are both connected in parallel to one end of a bidirectional relief valve and then connected to a motor drive mechanism. The other end of the first channel and the other end of the second channel are both connected in parallel to one end of a low-flow balance valve and then connected to the hydraulic control valve assembly.

4. The shield tunnel segment machine rotation hydraulic control device according to claim 3, characterized in that, One end of the first pilot port and one end of the second pilot port are connected in parallel to the first solenoid valve, and one end of the small flow balancing valve is connected to the proportional servo valve.

5. The shield tunnel segment machine rotation hydraulic control device according to claim 1, characterized in that, The motor drive mechanism includes a hydraulic motor, a segmenter gear ring rotating component, and a locking component. The hydraulic motor is connected to the segmenter gear ring rotating component, the locking component is coaxially connected to the hydraulic motor, and one end of the locking component is connected to a hydraulic control valve group.

6. A rotary hydraulic control device for a tunnel boring machine segment machine according to any one of claims 2-4, characterized in that, The proportional servo valve is a high-response dynamic proportional servo valve.

7. A rotary hydraulic control device for a tunnel boring machine segment machine according to any one of claims 2-4, characterized in that, Both the first and second solenoid valves are 2-position 4-way solenoid valves.

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