CN201288567Y - Shield cutter head hydraulic control system for expanding speed regulating range - Google Patents

Abstract

The utility model discloses a hydraulic control system of a shield cutter head which widens the range of speed regulation. The motor is rigidly connected to the constant pressure variable pump through a coupling, the oil outlet of the constant pressure variable pump is connected to the oil inlet of the main check valve, and the oil outlet of the main check valve is respectively connected to the oil inlet of the accumulator and the overflow valve. The oil ports are connected to four identical motor/pump components. The hydraulic motor/pump is connected in parallel in the circuit, and the power is provided by a constant pressure source composed of a constant pressure variable pump and an accumulator. The hydraulic motors/pumps are individually controlled, and the displacement and working status of each hydraulic motor/pump can be adjusted in real time according to different geological conditions to control the speed and torque of the cutter head. The system uses hydraulic motor/pump as the actuator to switch the working state of the motor and the pump. By controlling the number of actuators working in different states at the same time, the system can realize high and low speed operation under the condition that the displacement of the oil supply hydraulic pump remains unchanged. The interchangeability of conditions widens the range of speed regulation and enhances the adaptability of the cutter head drive system to different geological conditions.

Description

A Hydraulic Control System of Shield Tunneling Cutter with Widening Range of Speed Regulation

technical field

The utility model relates to a fluid pressure actuator, in particular to a hydraulic control system of a shield cutterhead with a widened speed regulation range.

Background technique

Shield boring machine is a modern high-tech excavation equipment specially used for underground tunnel construction. It is widely used in the construction of tunnel projects with complex and changeable geological conditions and harsh construction environments. Shield tunneling plays an irreplaceable role in other tunneling forms in the development and utilization of underground space. With the development of science and technology and social progress, shield tunneling will gradually replace traditional methods.

The cutter head is one of the key components of the shield tunneling machine, and its main functions are excavation, stabilization and stirring. Because the soil conditions of the excavation section vary greatly during the entire construction process, and the excavation depth is different, the cutting torque and speed required by the cutter head are very different, resulting in very complicated working conditions for the cutter head drive, with large driving power and a wide range of changes. .

Because the typical working condition of the cutter head is low speed and high torque when the shield tunnels in the soft ground, while the working condition of the shield tunneling in the hard ground is high speed and low torque. The design of the traditional cutter head drive hydraulic system takes these two working conditions into consideration, making the total installed power of the system very large. The low energy utilization rate of a system with such a large energy consumption under low load conditions has an extremely important impact on the overall performance of the system. Therefore, how to widen the speed regulation range of the cutter head drive system so that the system can adapt to various stratum excavation needs with a smaller total installed power is a key technical issue in the cutter head drive system.

Contents of the invention

In order to overcome the problems existing in the shield construction process and take into account the requirements of the overall performance of the system, the purpose of the utility model is to provide a shield cutter head drive hydraulic control system that widens the speed regulation range. Each hydraulic motor that drives the cutter head can switch the working state independently. In low-load conditions, the number of actuators working in the motor state can be reduced to achieve the purpose of using a smaller displacement pump to achieve high speed of the cutter head. Working at the same time The actuator in the pump state can also be used as a power source to drive the actuator in the motor state together with the hydraulic pump, which greatly increases the speed regulation range of the system. The cutter head can also realize stepless speed regulation by adjusting the displacement of the hydraulic pump and the actuator.

The technical solution adopted by the utility model to solve technical problems is:

The motor is rigidly connected to the constant pressure variable pump through a coupling, the oil suction port of the constant pressure variable pump is connected to the oil tank, the oil outlet of the constant pressure variable pump is connected to the oil inlet of the main check valve, and the oil outlet of the main check valve is respectively connected to the storage tank. The oil inlet of the energy generator, the oil inlet of the relief valve are connected with four groups of motor/pump components with the same structure, and the oil outlet of the relief valve is connected to the oil tank; the structure of the motor/pump of the first group is described as follows: total one-way The oil outlet of the valve, the oil inlet of the accumulator and the oil inlet of the relief valve are respectively connected to the _P1 port of the first three-position four-way reversing valve and the oil outlet of the first one-way valve; the second one-way valve and The oil outlet of the third one-way valve is connected to the oil inlet of the first one-way valve, the oil inlet of the fourth one-way valve is connected to the oil tank of the fifth one-way valve, and the oil inlet of the second one-way valve is connected. The port is connected with the oil outlet of the fourth one-way valve, and then respectively connected with the _B1 port of the first three-position four-way reversing valve and the first port of the first hydraulic motor/pump, and the oil inlet of the third one-way valve and the first port of the first hydraulic motor/pump. After the oil outlets of the five one-way valves are connected, they are respectively connected to port _A1 of the first three-position four-way reversing valve and the other port of the first hydraulic motor/pump, and port _T1 of the first three-position four-way reversing valve Connected with the T ₂ port, T ₃ port and T ₄ port of the second, third and fourth three-position four-way reversing valves, the output shaft of the first hydraulic motor/pump drives the cutter head to rotate through the first gear reducer G .

The beneficial effect that the utility model has is:

The actuator motor/pump of the hydraulic system is individually controlled. Each actuator drives the cutter head to rotate when it is working in the motor state, and supplies hydraulic oil to the system when it is working in the pump state. By combining and optimizing the working state of each actuator, the cutter head can be made The disc rotation speed has a larger adjustment range without increasing the specification of the hydraulic pump, which is better adapted to the complex geological environment.

Description of drawings

Accompanying drawing is the structural principle schematic diagram of the utility model.

In the figure: 1. Oil tank, 2. Motor, 3. Coupling, 4. Constant pressure variable pump, 5. Check valve, 6. Relief valve, 7. Accumulator, 8.1, 8.2, 8.3, 8.4, Three-position four-way reversing valve, 9.1, 9.2, 9.3, 9.4, 10.1, 10.2, 10.3, 10.4, 11.1, 11.2, 11.3, 11.4, 12.1, 12.2, 12.3, 12.4, 13.1, 13.2, 13.3, 13.4 are one-way Valves, 14.1, 14.2, 14.3, 14.4 are hydraulic motors/pumps, 15, cutter head, 16, 17, 18, 19, 20, 21, 22, 23, 24, 25, 26, 27, 28, 29, 30, 31, 32, 33, 34, 35, 36, 37, 38, 39, 40, 41, 42, 43, 44, 45, 46, 47, 48, 49, 50, 51, 52, 53, 54, 55, 56, 57, 58, 59, 60, 61, 62, 63, 64, 65, 66, 67 are pipelines.

Detailed ways

Below in conjunction with accompanying drawing and embodiment the utility model is further described.

As shown in the accompanying drawings, the motor 2 of the utility model is rigidly connected with the constant pressure variable pump 4 through the coupling 3, the oil suction port of the constant pressure variable pump 4 is connected with the oil tank 1 through the pipeline 18, and the oil outlet of the constant pressure variable pump 4 is connected through the pipe Road 19 is connected to the oil inlet of the main check valve 5, and the oil outlet of the main check valve 5 is respectively connected to the oil inlet of the accumulator 7, the oil inlet of the relief valve 6 and four groups of motors/pumps with the same structure through the pipeline 17 The components are connected, and the oil outlet of the overflow valve 6 is connected to the oil tank through the pipeline 16; the structure of the motor/pump of the first group is described as follows: the oil outlet of the total check valve 5, the oil inlet of the accumulator 7 and the overflow valve 6 The oil inlet is respectively connected to the _P1 port of the first three-position four-way reversing valve through the pipeline 20 and the oil outlet of the first one-way valve 9.1 through the pipeline 21; the second one-way valve 11.1 and the third one-way valve The oil outlet of 10.1 is connected through the pipeline 38 and then connected with the oil inlet of the first one-way valve 9.1 through the pipeline 39; The oil inlet of the second one-way valve 11.1 is connected through the pipeline 36 and the oil outlet of the fourth one-way valve 13.1 through the pipeline 37, and then respectively connected with the _B1 port of the first three-position four-way reversing valve and the first one through the pipeline 35. One port of the hydraulic motor/pump 14.1, the oil inlet of the third one-way valve 10.1 is connected through the pipeline 33 and the oil outlet of the fifth one-way valve 12.1 is connected through the pipeline 34, and then respectively connected to the first three-position four-way switch through the pipeline 32 A ₁ port of the directional valve and another port of the first hydraulic motor/pump 14.1, T ₁ port of the first three-position four-way reversing valve is connected with the second three-position four-way reversing valve through pipeline 28 and pipeline 29 Port _T2 of the second three-position four-way reversing valve is connected to port _T3 of the third _three- position four-way reversing valve through pipeline 29 and pipeline 30, and the third three-position four-way reversing valve The _T3 port of the first hydraulic motor/pump 14.1 is connected to the _T4 port of the fourth three-position four-way reversing valve through the pipeline 30 and the pipeline 31, and the output shaft of the first hydraulic motor/pump 14.1 drives the cutter head 15 to rotate through the first gear reducer G.

The motor/pump structure of the second group is described as follows: the oil outlet of the total check valve 5, the oil inlet of the accumulator 7 and the oil inlet of the overflow valve 6 are respectively connected to the second three-position four-way reversing valve through the pipeline 22 Port P ₂ is connected to the oil outlet of the sixth one-way valve 9.2 through the pipeline 23; the oil outlets of the seventh one-way valve 11.2 and the eighth one-way valve 10.2 are connected through the pipeline 48 and then connected to the sixth one-way valve through the pipeline 44 The oil inlet of 9.2, the oil inlet of the ninth one-way valve 13.2 and the tenth one-way valve 12.2 are connected and connected to the oil tank through the pipeline 49, and the oil inlet of the seventh one-way valve 11.2 is connected through the pipeline 46 and the ninth one-way valve The oil outlet of 13.2 is connected through the pipeline 47, and then respectively connected with the _B2 port of the second three-position four-way reversing valve and the first port of the second hydraulic motor/pump 14.2, and the oil inlet port of the eighth one-way valve 10.2 through the pipeline 45 The pipeline 42 and the oil outlet of the tenth one-way valve 12.2 are connected through the pipeline 43, and then respectively connected to the A2 port of the second three-position four-way reversing valve and the other port of the second hydraulic motor/pump 14.2 through the pipeline 41. The output shaft of the second hydraulic motor/pump 14.2 drives the cutter head 15 to rotate through the second gear reducer G.

The motor/pump structure of the third group is described as follows: the oil outlet of the total check valve 5, the oil inlet of the accumulator 7 and the oil inlet of the overflow valve 6 are respectively connected to the third three-position four-way reversing valve through the pipeline 24 Port P ₃ is connected to the oil outlet of the eleventh one-way valve 9.3 through the pipeline 25; The oil inlet of a one-way valve 9.3, the oil inlet of the fourteenth one-way valve 13.3 and the fifteenth one-way valve 12.3 are connected and connected to the oil tank through the pipeline 58, and the oil inlet of the twelfth one-way valve 11.3 is connected through the pipeline 54 and the oil outlet of the fourteenth one-way valve 13.3 are connected through the pipeline 53, and then respectively connected to the _B3 port of the third three-position four-way reversing valve and a port of the third hydraulic motor/pump 14.3 through the pipeline 56, the tenth The oil inlet of the three one-way valves 10.3 is connected through the pipeline 51 and the oil outlet of the fifteenth one-way valve 12.3 through the pipeline 52, and then respectively connected to the _A3 port and the third three-position four-way reversing valve through the pipeline 50. The other port of the hydraulic motor/pump 14.3, the output shaft of the third hydraulic motor/pump 14.3 drives the cutter head 15 to rotate through the third gear reducer G.

The motor/pump structure of the fourth group is described as follows: the oil outlet of the total check valve 5, the oil inlet of the accumulator 7 and the oil inlet of the overflow valve 6 are respectively connected to the fourth three-position four-way reversing valve through the pipeline 26 Port P ₄ is connected to the oil outlet of the sixteenth one-way valve 9.4 through the pipeline 27; The oil inlet of the six one-way valve 9.4, the oil inlet of the nineteenth one-way valve 13.4 and the twentieth one-way valve 12.4 are connected to each other and connected to the oil tank through the pipeline 66, and the oil inlet of the seventeenth one-way valve 11.4 is connected through the pipeline 63 and the oil outlet of the nineteenth one-way valve 13.4 are connected through the pipeline 62, and then respectively connected to the _B4 port of the fourth three-position four-way reversing valve and a port of the fourth hydraulic motor/pump 14.4 through the pipeline 64, the tenth The oil inlet of the eighth one-way valve 10.4 is connected through the pipeline 60 and the oil outlet of the twentieth one-way valve 12.4 is connected through the pipeline 61, and then the _A4 port and the fourth one of the fourth three-position four-way reversing valve are respectively connected through the pipeline 59. The other port of the hydraulic motor/pump 14.4, the output shaft of the third hydraulic motor/pump 14.4 drives the cutter head 15 to rotate through the fourth gear reducer G.

The working principle of the utility model is as follows:

The motor 2 is powered on to drive the constant pressure variable pump 4 to rotate. The oil suction port of the constant pressure variable pump 4 sucks oil from the oil tank 1. Pipeline 27, a part of oil liquid enters the oil inlet of overflow valve 6 and accumulator 7 and pipelines 20, 21, 22, 23, 24, 25, 26, 27 at the same time.

During shield excavation, if the condition of soft ground is encountered, the working condition of the cutter head is low speed and high torque. At this time, four sets of motors/pumps work at the same time to make the system output high torque. Since the working principles of the four groups of motors/pumps are the same, the first group is taken as an example for illustration.

Three-position four-way reversing valve 8.1 left electromagnet is energized, and the high-pressure oil in pipeline 27 flows into the three-position four-way reversing valve 8.1P1 port, three-position four-way reversing valve 8.1A1 port, and pipeline 32 Motor/pump 14.1 oil port at one end, motor/pump 14.1 oil port at the other end hydraulic oil flows back to the oil tank through pipeline 35, three-position four-way reversing valve 8.1B1 port, three-position four-way reversing valve 8.1T1 port, and pipeline 28 . A part of the high-pressure oil in the pipeline 32 passes through the check valve 10.1, the pipeline 38, and the pipeline 39 to the oil inlet of the check valve 9.1. Since the high-pressure oil in the pipeline 27 passes through the pipeline 21 to the oil outlet of the check valve 9.1, its pressure is slightly higher than the pressure of the hydraulic oil in the pipeline 38 after the throttling loss at the reversing valve port, so the check valve 9.1 does not Open. At this moment, the cutter head rotates in the forward direction.

Three-position four-way reversing valve 8.1 right solenoid is energized, and the high-pressure oil in pipeline 27 flows into the three-position four-way reversing valve 8.1P1 port, three-position four-way reversing valve 8.1B1 port, and pipeline 35 The oil port at the other end of the motor/pump 14.1, the hydraulic oil at the oil port at the one end of the motor/pump 14.1 flows back to the oil tank through the pipeline 32, the 8.1A1 port of the three-position four-way reversing valve, the 8.1T1 port of the three-position four-way reversing valve, and the pipeline 28 . A part of the high-pressure oil in the pipeline 35 passes through the check valve 11.1, the pipeline 38, and the pipeline 39 to the oil inlet of the check valve 9.1. Since the high-pressure oil in the pipeline 27 passes through the pipeline 21 to the oil outlet of the check valve 9.1, its pressure is slightly higher than the pressure of the hydraulic oil in the pipeline 38 after the throttling loss at the reversing valve port, so the check valve 9.1 does not Open. At this time, the cutter head rotates in the opposite direction.

When shield tunneling encounters hard rock formation conditions, the cutterhead works at high speed and low torque. At this time, without increasing the displacement of the constant pressure variable pump, the output speed of the system is increased by changing the working state of the motor/pump. In actual work, the number of motor/pump actuators working in the pump state and motor state can be determined according to the working conditions, and the drive elements should be evenly arranged along the circumference of the main bearing of the cutter head as far as possible to reduce the eccentric effect. The switching of the working state of the motor/pump is realized by controlling the power on and off of the electromagnet of the three-position four-way reversing valve. In the following, the second group of motors/pumps works in the pump state, and the other groups of motors/pumps work in the motor state as an example. The principle of the system working in the motor state is the same as the above situation.

When the motor/pump 14.1, 14.3, 14.4 rotates in the forward direction, the gear reducer drives the cutter head 15 to rotate in the forward direction. Since the motor/pump 14.2 and the cutter head 15 are rigidly connected together through the reducer gear, the motor/pump 14.2 is rotating Driven by the cutter head 15, it is forced to rotate forwardly. At this time, the three-position four-way reversing valve 8.2 electromagnet is de-energized, the pipeline 41 and the pipeline 45 are cut off, and a certain negative pressure is formed in a short period of time in the pipeline 41. The hydraulic oil in the oil tank reaches the oil port at one end of the motor/pump 14.2 through the pipeline 49, the check valve 12.2, and the pipeline 43, and passes through the oil port at the other end of the motor/pump 14.2 through the pipeline 46, the check valve 11.2, the pipeline 48, the pipeline Road 44, check valve 9.2, pipeline 23 flow back in the main oil circuit 27. The increase in hydraulic oil flow in the main oil circuit 27 and the reduction in the number of actuator motor/pump elements working in the motor state enable the system to achieve a wide range of speed regulation without increasing the displacement of the main drive pump.

When the motors/pumps 14.1, 14.3, and 14.4 rotate in the reverse direction, the gear reducer drives the cutter head 15 to rotate in the reverse direction. Since the motor/pump 14.2 and the cutter head 15 are rigidly connected together through the reducer gear, the motor/pump 14.2 is rotating Driven by the cutterhead 15, it is forced to rotate in the opposite direction. At this time, the three-position four-way reversing valve 8.2 electromagnet is de-energized, the pipeline 41 and the pipeline 45 are cut off, and a certain negative pressure is formed in a short period of time in the pipeline 45. The hydraulic oil in the oil tank reaches the oil port at the other end of the motor/pump 14.2 through the pipeline 49, the check valve 13.2, and the pipeline 47, and passes through the oil port at the one end of the motor/pump 14.2 through the pipeline 42, the check valve 10.2, the pipeline 48, the pipeline Road 44, check valve 9.2, pipeline 23 flow back in the main oil circuit 27.

When the shield cutter head needs to stop rotating, the three-position four-way reversing valves 8.1, 8.2, 8.3, and 8.4 electromagnets are powered off, and all hydraulic motors/pumps continue to rotate instantly under the inertia of the rotating shield cutter head, and then follow the The same working principle as that of the above-mentioned hydraulic motor/pump 14.2 under the condition that the electromagnet of the three-position four-way reversing valve 8.2 is de-energized completes the braking process, and feeds the braking energy back into the main oil circuit 27 .

The above-mentioned specific embodiments are used to explain the utility model, rather than to limit the utility model. Within the spirit of the utility model and the scope of protection of the claims, any modifications and changes made to the utility model fall into the scope of the utility model. scope of protection.

Claims (1)

1. A shield cutter head hydraulic control system that widens the range of speed regulation, characterized in that: the motor (2) is rigidly connected to the constant pressure variable pump (4) via a coupling (3), and the constant pressure variable pump (4) The oil suction port is connected to the oil tank (1), the oil outlet of the constant pressure variable pump (4) is connected to the oil inlet of the main check valve (5), and the oil outlet of the main check valve (5) is respectively connected to the accumulator (7) The oil inlet and overflow valve (6) oil inlet are connected to four groups of motor/pump components with the same structure, and the oil outlet of overflow valve 6 is connected to the oil tank; the structure of the first group of motor/pump is described as follows: The oil outlet of the check valve (5), the oil inlet of the accumulator (7) and the oil inlet of the relief valve (6) are respectively connected to the _P1 port of the first three-position four-way reversing valve (8.1) and the first The oil outlet of the one-way valve (9.1); the oil outlet of the second one-way valve (11.1) and the third one-way valve (10.1) are connected to the oil inlet of the first one-way valve (9.1), and the fourth The one-way valve (13.1) is connected to the oil inlet of the fifth one-way valve (12.1) and then connected to the oil tank, and the oil inlet of the second one-way valve (11.1) is connected to the oil outlet of the fourth one-way valve (13.1) Then respectively connect the _B1 port of the first three-position four-way reversing valve (8.1) and the first port of the first hydraulic motor/pump (14.1), the oil inlet port of the third one-way valve (10.1) and the fifth one-way After the oil outlets of the valve (12.1) are connected, they are respectively connected to the _A1 port of the first three-position four-way reversing valve (8.1) and the other port of the first hydraulic motor/pump (14.1). Port T ₁ of the directional valve (8.1) is connected to ports T ₂ , T ₃ and T ₄ of the second, third and fourth three-position four-way reversing valves, and the output of the first hydraulic motor/pump (14.1) The shaft drives the cutter head (15) to rotate through the first gear reducer G.

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